CN102460026B - Ceiling-mounted air conditioning unit - Google Patents

Ceiling-mounted air conditioning unit Download PDF

Info

Publication number
CN102460026B
CN102460026B CN201080026832.0A CN201080026832A CN102460026B CN 102460026 B CN102460026 B CN 102460026B CN 201080026832 A CN201080026832 A CN 201080026832A CN 102460026 B CN102460026 B CN 102460026B
Authority
CN
China
Prior art keywords
heat
transfer pipe
row
pipe
cold
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Active
Application number
CN201080026832.0A
Other languages
Chinese (zh)
Other versions
CN102460026A (en
Inventor
坂下朗彦
吉冈俊
道辻善治
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Daikin Industries Ltd
Original Assignee
Daikin Industries Ltd
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Daikin Industries Ltd filed Critical Daikin Industries Ltd
Publication of CN102460026A publication Critical patent/CN102460026A/en
Application granted granted Critical
Publication of CN102460026B publication Critical patent/CN102460026B/en
Active legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Images

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F1/00—Room units for air-conditioning, e.g. separate or self-contained units or units receiving primary air from a central station
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D1/00—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators
    • F28D1/02—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid
    • F28D1/04—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits
    • F28D1/0408—Multi-circuit heat exchangers, e.g. integrating different heat exchange sections in the same unit or heat exchangers for more than two fluids
    • F28D1/0417—Multi-circuit heat exchangers, e.g. integrating different heat exchange sections in the same unit or heat exchangers for more than two fluids with particular circuits for the same heat exchange medium, e.g. with the heat exchange medium flowing through sections having different heat exchange capacities or for heating/cooling the heat exchange medium at different temperatures
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F1/00—Room units for air-conditioning, e.g. separate or self-contained units or units receiving primary air from a central station
    • F24F1/0007—Indoor units, e.g. fan coil units
    • F24F1/0043—Indoor units, e.g. fan coil units characterised by mounting arrangements
    • F24F1/0047—Indoor units, e.g. fan coil units characterised by mounting arrangements mounted in the ceiling or at the ceiling
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F1/00—Room units for air-conditioning, e.g. separate or self-contained units or units receiving primary air from a central station
    • F24F1/0007—Indoor units, e.g. fan coil units
    • F24F1/0059—Indoor units, e.g. fan coil units characterised by heat exchangers
    • F24F1/0063—Indoor units, e.g. fan coil units characterised by heat exchangers by the mounting or arrangement of the heat exchangers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F1/00—Room units for air-conditioning, e.g. separate or self-contained units or units receiving primary air from a central station
    • F24F1/0007—Indoor units, e.g. fan coil units
    • F24F1/0059—Indoor units, e.g. fan coil units characterised by heat exchangers
    • F24F1/0067—Indoor units, e.g. fan coil units characterised by heat exchangers by the shape of the heat exchangers or of parts thereof, e.g. of their fins
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F1/00—Room units for air-conditioning, e.g. separate or self-contained units or units receiving primary air from a central station
    • F24F1/0007—Indoor units, e.g. fan coil units
    • F24F1/0071—Indoor units, e.g. fan coil units with means for purifying supplied air
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F13/00—Details common to, or for air-conditioning, air-humidification, ventilation or use of air currents for screening
    • F24F13/32—Supports for air-conditioning, air-humidification or ventilation units
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B39/00—Evaporators; Condensers
    • F25B39/02—Evaporators
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D1/00—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators
    • F28D1/02—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid
    • F28D1/04—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits
    • F28D1/047—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being bent, e.g. in a serpentine or zig-zag
    • F28D1/0477—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being bent, e.g. in a serpentine or zig-zag the conduits being bent in a serpentine or zig-zag
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F27/00—Control arrangements or safety devices specially adapted for heat-exchange or heat-transfer apparatus
    • F28F27/02—Control arrangements or safety devices specially adapted for heat-exchange or heat-transfer apparatus for controlling the distribution of heat-exchange media between different channels
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D21/00—Heat-exchange apparatus not covered by any of the groups F28D1/00 - F28D20/00
    • F28D2021/0019—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for
    • F28D2021/0068—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for for refrigerant cycles
    • F28D2021/0071—Evaporators

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Air Filters, Heat-Exchange Apparatuses, And Housings Of Air-Conditioning Units (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
  • Other Air-Conditioning Systems (AREA)

Abstract

An indoor heat exchanger (42) which is housed inside an indoor unit (4) serving as a ceiling-mounted air conditioning unit has a plurality of heat-transfer pipes (71, 72, 73) arranged in three rows in multiple stages in the vertical direction and in the flow direction of air which is blown out from an indoor fan (41). When the air conditioning unit is set to cooling mode, a plurality of liquid coolant pipes (91) on the coolant inlet side are connected to the heat-transfer pipes (71) in the first row, gas coolant pipes (92) in the second row which constitute some of a plurality of gas coolant pipes (92, 93) on the coolant outlet side are connected to the heat-transfer pipes (72) in the second row, and gas coolant pipes (93) in the third row which constitute the remainder of the plurality of gas coolant pipes (92, 93) are connected to the heat-transfer pipes (73) in the third row.

Description

Ceiling built-in air-conditioning system
Technical field
The present invention relates to a kind of ceiling built-in air-conditioning system, especially, relate to a kind of ceiling built-in air-conditioning system of structure that there is the indoor heat converter being formed by fin tube type heat exchanger and be disposed at the outer circumferential side of overlooking the centrifugal blower while observing.
Background technology
In the past, there is a kind of ceiling built-in air-conditioning system as shown in patent documentation 1 (Japanese Patent Laid-Open 2009-30827 communique).This ceiling built-in air-conditioning system has the indoor heat converter consisting of fin tube type heat exchanger and is disposed at the structure of outer circumferential side of overlooking the centrifugal blower while observing.In indoor heat converter, many heat-transfer pipes that flow therein for cold-producing medium are arranged in multistage (multirow) on above-below direction, and are arranged with two row in the flow direction of the air blowing out from centrifugal blower.
Summary of the invention
In above-mentioned existing ceiling built-in air-conditioning system, require further high performance.In addition, for the requirement of this high performance, in ceiling built-in air-conditioning system, consider the restriction of height dimension, planar dimension, can consider the columns of the heat-transfer pipe that forms indoor heat converter to change into three row by two row.Now, can consider to adopt following structure: when refrigeration, making cold-producing medium is that the heat-transfer pipe of first row, the heat-transfer pipe of secondary series, the row of downwind side are the sequential flowing of tertial heat-transfer pipe according to the row of weather side in the flow direction of air, when heating, make cold-producing medium according to the sequential flowing contrary with when refrigeration.
But in this indoor heat converter of heat-transfer pipe being made to three row, when refrigeration, air and cold-producing medium become concurrent flow, therefore, the temperature that flows through the air of the 3rd biographies heat pipe has the tendency of reduction.Therefore, in this indoor heat converter, the degree of superheat of the cold-producing medium at the refrigerant outlet place working as the evaporimeter of cold-producing medium when refrigeration is not variable large, and heat exchanger effectiveness during refrigeration may not can improve.
Technical problem of the present invention is to be disposed in the ceiling built-in air-conditioning system of structure of the outer circumferential side of overlooking the centrifugal blower while observing having the indoor heat converter consisting of fin tube type heat exchanger, make the degree of superheat of the cold-producing medium at the refrigerant outlet place working as the evaporimeter of cold-producing medium when refrigeration easily become large, the heat exchanger effectiveness while freezing to improve.
The ceiling built-in air-conditioning system of the first invention is the ceiling built-in air-conditioning system of structure that has the indoor heat converter consisting of fin tube type heat exchanger and be disposed at the outer circumferential side of overlooking the centrifugal blower while observing.Indoor heat converter has following structure: many heat-transfer pipes that flow therein for cold-producing medium are arranged in multistage on above-below direction, and are arranged with three row in the flow direction of the air blowing out from centrifugal blower.In addition, indoor heat converter has following structure: the refrigerant inlet at the indoor heat converter of when refrigeration indoor heat converter working as the evaporimeter of cold-producing medium is connected with many liquid refrigerant pipes, and these many liquid refrigerant pipes are connected with the heat-transfer pipe that the row of weather side in the flow direction of air are first row.In addition, indoor heat converter has following structure: when refrigeration, the refrigerant outlet of indoor heat converter is connected with many gas refrigerant pipes, and the part in these many gas refrigerant pipes is that secondary series side gas refrigerant pipe is connected with the heat-transfer pipe of secondary series in the flow direction of air.In addition, indoor heat converter has following structure: the remainder in many gas refrigerant pipes i.e. the 3rd row side gas refrigerant pipe is that tertial heat-transfer pipe is connected with the row of downwind side in the flow direction of air.
Therefore, in this ceiling built-in air-conditioning system, during refrigeration, a part for the cold-producing medium that refrigerant inlet during from the refrigeration of indoor heat converter flows into, just having carried out heat exchange with the air of the temperature heat-transfer pipe that passes across secondary series higher than the air that passes across tertial heat-transfer pipe, is just transported to secondary series side gas refrigerant pipe.In addition, in this ceiling built-in air-conditioning system, during refrigeration, the remainder of the cold-producing medium that the refrigerant inlet during from the refrigeration of indoor heat converter flows into, just having carried out heat exchange with the air that passes across tertial heat-transfer pipe, is just transported to the 3rd row side gas refrigerant pipe.In addition, flow through cold-producing medium after secondary series side gas refrigerant pipe and the cold-producing medium interflow of flowing through after the 3rd row side gas refrigerant pipe, and the refrigerant outlet during from the refrigeration of indoor heat converter flows out.At this, because the degree of superheat of just having carried out the cold-producing medium after heat exchange with the air of heat-transfer pipe that passes across secondary series is subject to the temperature impact of the air of the heat-transfer pipe that passes across secondary series, therefore easily than just and the air that passes across tertial heat-transfer pipe to have carried out the degree of superheat of the cold-producing medium after heat exchange large.
By this, in this ceiling built-in air-conditioning system, the degree of superheat of the cold-producing medium that the refrigerant outlet during from the refrigeration of indoor heat converter flows out is compared easy increase with adopting the structure that all tertial heat-transfer pipes of gas refrigerant Guan Douyu are connected, thereby can improve the heat exchanger effectiveness while freezing.
In addition, in this ceiling built-in air-conditioning system, while heating, the cold-producing medium that the refrigerant inlet during from the heating of indoor heat converter flows into be all just and the air of the minimum heat-transfer pipe that passes across first row of temperature be just transported to liquid refrigerant pipe having carried out heat exchange.
By this, in this ceiling built-in air-conditioning system, the degree of supercooling of refrigerant outlet during the heating of indoor heat converter is difficult for diminishing, thus the reduction of the heat exchanger effectiveness in the time of heating.
As mentioned above, in this ceiling built-in air-conditioning system, the degree of supercooling of the refrigerant outlet while making the heating of indoor heat converter is difficult for reducing, and the degree of superheat of the cold-producing medium that flows out of the refrigerant outlet while making the refrigeration from indoor heat converter easily increases, thereby the reduction of the heat exchanger effectiveness of the indoor heat converter in the time of heating, and can improve the heat exchanger effectiveness of the indoor heat converter in when refrigeration.
The ceiling built-in air-conditioning system of the second invention is on the basis of the ceiling built-in air-conditioning system of the first invention, length direction one end connection of liquid refrigerant pipe, secondary series side gas refrigerant pipe and the 3rd row side gas refrigerant pipe and corresponding heat-transfer pipe.
In this ceiling built-in air-conditioning system, can be integrated into that the length direction one of indoor heat converter is distolateral carries out the connection operation towards heat-transfer pipe of liquid refrigerant pipe, secondary series side gas refrigerant pipe and the 3rd row side gas refrigerant pipe, therefore, improved the assembleability of indoor heat converter.
The ceiling built-in air-conditioning system of the 3rd invention is on the basis of the ceiling built-in air-conditioning system of the first invention or the second invention, indoor heat converter has branching portion between row, and between these row, branching portion is branched off into the cold-producing medium that is transported to the outlet of the heat-transfer pipe of first row when freezing heat-transfer pipe and the tertial heat-transfer pipe of secondary series.In addition in the outlet of the heat-transfer pipe of the secondary series of when refrigeration indoor heat converter working as the evaporimeter of cold-producing medium, be connected with secondary series side gas refrigerant pipe.In addition in the outlet of the tertial heat-transfer pipe of when refrigeration indoor heat converter working as the evaporimeter of cold-producing medium, be connected with the 3rd row side gas refrigerant pipe.
In this ceiling built-in air-conditioning system, during refrigeration, by in the heat-transfer pipe of first row because carrying out heat exchange and be transported in the cold-producing medium branch of rich gas state heat-transfer pipe and the tertial heat-transfer pipe of secondary series with air, therefore, the flow velocity that can suppress the cold-producing medium in rich gas state increases.In addition, in this ceiling built-in air-conditioning system, while heating, make in the heat-transfer pipe of secondary series because of with air carry out in the cold-producing medium of heat exchange in rich solution state and tertial heat-transfer pipe because carrying out the cold-producing medium interflow of heat exchange in rich solution state with air, and be delivered to the heat-transfer pipe of first row, therefore, can make the flow velocity of the cold-producing medium in rich solution state increase the pyroconductivity of the heat-transfer pipe of first row.
By this, in this ceiling built-in air-conditioning system, because making cold-producing medium flow branching, branching portion between being listed as by utilization suppresses the increase of the pressure loss, the heat exchanger effectiveness of the indoor heat converter in the time of therefore further improving refrigeration.Especially, in this ceiling built-in air-conditioning system, the flow velocity that can suppress the cold-producing medium in heat-transfer pipe and the tertial heat-transfer pipe of the secondary series that the cold-producing medium of the rich gas state larger on the impact of the pressure loss flows through increases, the heat exchanger effectiveness of the indoor heat converter in the time of therefore, effectively improving refrigeration.In addition, in this ceiling built-in air-conditioning system, make the flow velocity of the cold-producing medium in the heat-transfer pipe of the first row that the cold-producing medium of the rich solution state less on the impact of the pressure loss flows through increase pyroconductivity, therefore, it is large that the degree of supercooling of refrigerant outlet during the heating of indoor heat converter easily becomes, thus the reduction of the heat exchanger effectiveness in the time of further suppressing to heat.
The ceiling built-in air-conditioning system of the 4th invention is on the basis of ceiling built-in air-conditioning system of the 3rd invention, flows through a heat-transfer pipe the first upstream side heat-transfer pipe in the heat-transfer pipe that cold-producing medium after liquid refrigerant pipe is transported to first row during refrigeration.The cold-producing medium that is transported to the first upstream side heat-transfer pipe is flowing through after the first upstream side heat-transfer pipe, also flows through the i.e. first downstream heat-transfer pipe of heat-transfer pipe of the described first row different from the first upstream side heat-transfer pipe.The cold-producing medium that flows through the first downstream heat-transfer pipe is a heat-transfer pipe i.e. three upstream side heat-transfer pipe in second upstream side heat-transfer pipe and tertial heat-transfer pipe by Lie Jian branching portion branch to a heat-transfer pipe in the heat-transfer pipe of secondary series in the outlet of the first downstream heat-transfer pipe.In addition, the cold-producing medium that is transported to the second upstream side heat-transfer pipe is flowing through after the second upstream side heat-transfer pipe, also flow through the i.e. second downstream heat-transfer pipe of heat-transfer pipe of the secondary series different from the second upstream side heat-transfer pipe, and be transported to secondary series side gas refrigerant pipe from the outlet of the second downstream heat-transfer pipe.In addition, the cold-producing medium that is transported to the 3rd upstream side heat-transfer pipe is flowing through after the 3rd upstream side heat-transfer pipe, also flow through i.e. the 3rd downstream heat-transfer pipe of the tertial heat-transfer pipe different from the 3rd upstream side heat-transfer pipe, and be transported to the 3rd row side gas refrigerant pipe from the outlet of the 3rd downstream heat-transfer pipe.
In this ceiling built-in air-conditioning system, in each biographies heat pipe, mobile cold-producing medium to turn back to the mode of one end and to flow from the length direction other end from length direction one end of indoor heat converter flows to the other end.Therefore, it is distolateral that not only liquid refrigerant pipe, secondary series side gas refrigerant pipe and the 3rd row side gas refrigerant pipe are integrated into the length direction one of indoor heat converter, and it is distolateral that between row, branching portion is also configured in the length direction one of indoor heat converter.
By this, in this ceiling built-in air-conditioning system, between need being listed as when assembling indoor heat converter in employing, branching portion is towards the structure of the connection operation of heat-transfer pipe, can be integrated into the distolateral branching portion that carries out between liquid refrigerant pipe, secondary series side gas refrigerant pipe, the 3rd row side gas refrigerant pipe and row of the length direction one of indoor heat converter towards the connection operation of heat-transfer pipe, therefore, can improve the assembleability of indoor heat converter.
The ceiling built-in air-conditioning system of the 5th invention is that the second upstream side heat-transfer pipe is disposed at the downside of the 3rd upstream side heat-transfer pipe on the basis of the ceiling built-in air-conditioning system of the 4th invention.
Therefore,, in this ceiling built-in air-conditioning system, when refrigeration, because making cold-producing medium, the effect of gravity more easily flows in large quantities the second upstream side heat-transfer pipe compared with the 3rd upstream side heat-transfer pipe.
By this, in this ceiling built-in air-conditioning system, it is large that the degree of superheat of the cold-producing medium that the refrigerant outlet during from the refrigeration of indoor heat converter flows out easily becomes, thus the heat exchanger effectiveness of the indoor heat converter in the time of further improving refrigeration.
The ceiling built-in air-conditioning system of the 6th invention is that between row, branching portion is formed as on the basis of ceiling built-in air-conditioning system of the 4th invention or the 5th invention: the flow path length till the entrance that exports to the second upstream side heat-transfer pipe of the first downstream heat-transfer pipe from the indoor heat converter when in refrigeration of the flow path length till the entrance that exports to the 3rd upstream side heat-transfer pipe of the first downstream heat-transfer pipe works as the evaporimeter of cold-producing medium is long.
In this ceiling built-in air-conditioning system, during refrigeration, easily there is more flow of refrigerant till arrive via branching portion between row from the outlet of the first heat-transfer pipe the second upstream side heat-transfer pipe that the flow path resistance of entrance is less.
By this, in this ceiling built-in air-conditioning system, it is large that the degree of superheat of the cold-producing medium that the refrigerant outlet during from the refrigeration of indoor heat converter flows out easily becomes, thus the heat exchanger effectiveness of the indoor heat converter in the time of further improving refrigeration.
The ceiling built-in air-conditioning system of the 7th invention is that on the basis of the ceiling built-in air-conditioning system of arbitrary invention in the 4th invention is invented to the 6th, the 3rd downstream heat-transfer pipe is disposed at the upside of the 3rd upstream side heat-transfer pipe.
In this ceiling built-in air-conditioning system, during refrigeration, the cold-producing medium that flows through the 3rd upstream side heat-transfer pipe and the 3rd downstream heat-transfer pipe flows in the mode rising smoothly towards the 3rd row side gas refrigerant pipe.
By this, in this ceiling built-in air-conditioning system, the increase of the pressure loss in the time of suppressing cold-producing medium and flow through the 3rd upstream side heat-transfer pipe and the 3rd downstream heat-transfer pipe, therefore, the heat exchanger effectiveness of the indoor heat converter in the time of further improving refrigeration.
The ceiling built-in air-conditioning system of the 8th invention is that on the basis of the ceiling built-in air-conditioning system of arbitrary invention in the 4th invention is invented to the 7th, the second downstream heat-transfer pipe is disposed at the upside of the second upstream side heat-transfer pipe.
In this ceiling built-in air-conditioning system, during refrigeration, the cold-producing medium that flows through the second upstream side heat-transfer pipe and the second downstream heat-transfer pipe flows in the mode rising smoothly towards secondary series side gas refrigerant pipe.
By this, in this ceiling built-in air-conditioning system, the increase of the pressure loss in the time of suppressing cold-producing medium and flow through the second upstream side heat-transfer pipe and the second downstream heat-transfer pipe, therefore, the heat exchanger effectiveness of the indoor heat converter in the time of further improving refrigeration.
The ceiling built-in air-conditioning system of the 9th invention is that on the basis of the ceiling built-in air-conditioning system of arbitrary invention in the 4th invention is invented to the 8th, the first downstream heat-transfer pipe is disposed at the upside of the first upstream side heat-transfer pipe.
In this ceiling built-in air-conditioning system, while heating, the cold-producing medium that flows through the first downstream heat-transfer pipe and the first upstream side heat-transfer pipe flows in the mode declining towards liquid refrigerant pipe.
By this, in this ceiling built-in air-conditioning system, it is large that the degree of supercooling of refrigerant outlet during the heating of indoor heat converter easily becomes, thus the reduction of the heat exchanger effectiveness in the time of further suppressing to heat.
The ceiling built-in air-conditioning system of the tenth invention is on the basis of ceiling built-in air-conditioning system of the 4th invention, and when refrigeration, the outlet of second downstream heat-transfer pipe and the outlet of three downstream heat-transfer pipe of indoor heat converter working as the evaporimeter of cold-producing medium is configured to adjacent with the outlet of another the second downstream heat-transfer pipe and the outlet of the 3rd downstream heat-transfer pipe that are disposed at upside or downside.In addition, at the entrance of the first upstream side heat-transfer pipe of when refrigeration indoor heat converter working as the evaporimeter of cold-producing medium, be configured to adjacent with the entrance of another the first upstream side heat-transfer pipe that is disposed at upside or downside.
In this ceiling built-in air-conditioning system, the second downstream heat-transfer pipe that temperature uprises and the 3rd downstream heat-transfer pipe centralized configuration are on fin, and the first upstream side heat-transfer pipe centralized configuration of temperature step-down is on fin.Therefore, in this ceiling built-in air-conditioning system, during refrigeration, the high heat of the second downstream heat-transfer pipe and the 3rd downstream heat-transfer pipe is difficult for being passed to via fin the other parts of fin, while heating, the heat of cooling of the first upstream side heat-transfer pipe is difficult for being passed to via fin the other parts of fin.
By this, in this ceiling built-in air-conditioning system, can do one's utmost to suppress because of the heat conduction via fin produces while freezing and while heating indoor heat converter the reduction of heat exchanger effectiveness.
The ceiling built-in air-conditioning system of the 11 invention is on the basis of ceiling built-in air-conditioning system of the 3rd invention, flows through a heat-transfer pipe the first upstream side heat-transfer pipe in the heat-transfer pipe that cold-producing medium after liquid refrigerant pipe is transported to first row during refrigeration.The cold-producing medium that is transported to the first heat-transfer pipe is flowing through after the first heat-transfer pipe, in the outlet of the first heat-transfer pipe, by Lie Jian branching portion branch, to a heat-transfer pipe in the heat-transfer pipe of secondary series, is i.e. the 3rd heat-transfer pipe of a heat-transfer pipe in the second heat-transfer pipe and tertial heat-transfer pipe.In addition, the cold-producing medium that is transported to the second heat-transfer pipe is flowing through after the second heat-transfer pipe, from the outlet of the second heat-transfer pipe, is transported to secondary series side gas refrigerant pipe.In addition, the cold-producing medium that is transported to the 3rd heat-transfer pipe is flowing through after the 3rd heat-transfer pipe, from the outlet of the 3rd heat-transfer pipe, is transported to the 3rd row side gas refrigerant pipe.
In this ceiling built-in air-conditioning system, cold-producing medium flows to the other end in the length direction one end from indoor heat converter, the length direction other end of indoor heat converter with branching portion between row in branch or interflow turn back to the mode of one end and flow from the length direction other end of indoor heat converter.Therefore for the path of flow of refrigerant, be, the shorter path of round trip on the length direction of indoor heat converter only.
By this, in this ceiling built-in air-conditioning system, can suppress the increase of the pressure loss, therefore, the heat exchanger effectiveness of the indoor heat converter while can further improve refrigeration, in addition, the reduction of the heat exchanger effectiveness of the indoor heat converter in the time of can also further suppressing to heat.
The ceiling built-in air-conditioning system of the 12 invention is that the second heat-transfer pipe is disposed at the downside of the 3rd heat-transfer pipe on the basis of the ceiling built-in air-conditioning system of the 11 invention.
In this ceiling built-in air-conditioning system, when refrigeration, because making cold-producing medium, the effect of gravity more easily flows in large quantities the second heat-transfer pipe compared with the 3rd heat-transfer pipe.
By this, in this ceiling built-in air-conditioning system, it is large that the degree of superheat of the cold-producing medium that the refrigerant outlet during from the refrigeration of indoor heat converter flows out easily becomes, thus the heat exchanger effectiveness of the indoor heat converter in the time of further improving refrigeration.
The ceiling built-in air-conditioning system of the 13 invention is that between row, branching portion is formed as on the basis of ceiling built-in air-conditioning system of the 11 invention or the 12 invention: the flow path length till the entrance that exports to the second heat-transfer pipe of the first heat-transfer pipe from the indoor heat converter when in refrigeration of the flow path length till the entrance that exports to the 3rd heat-transfer pipe of the first heat-transfer pipe works as the evaporimeter of cold-producing medium is long.
In this ceiling built-in air-conditioning system, during refrigeration, easily there is more flow of refrigerant till arrive via branching portion between row from the outlet of the first heat-transfer pipe the second heat-transfer pipe that the flow path resistance of entrance is less.
By this, in this ceiling built-in air-conditioning system, it is large that the degree of superheat of the cold-producing medium that the refrigerant outlet during from the refrigeration of indoor heat converter flows out easily becomes, thus the heat exchanger effectiveness of the indoor heat converter in the time of further improving refrigeration.
The ceiling built-in air-conditioning system of the 14 invention is on the basis of ceiling built-in air-conditioning system of the first invention or the second invention, and the cold-producing medium that flows through many part secondary series side liquid refrigerant pipes in liquid refrigerant pipe during refrigeration is transported to a heat-transfer pipe secondary series side heat-transfer pipe in the heat-transfer pipe of first row.The cold-producing medium that is transported to secondary series side heat-transfer pipe is flowing through after secondary series side heat-transfer pipe, the outlet of secondary series side heat-transfer pipe by secondary series in the heat-transfer pipe of branching portion branch to two secondary series.The cold-producing medium that is transported to the heat-transfer pipe of two secondary series is flowing through after the heat-transfer pipe of two secondary series, from the outlet of the heat-transfer pipe of two secondary series, is transported to secondary series side gas refrigerant pipe.During refrigeration, flow through heat-transfer pipe the 3rd row side heat-transfer pipe that cold-producing medium after many remainders in liquid refrigerant pipe the 3rd row side liquid refrigerant pipe is transported to the first row different from secondary series side heat-transfer pipe.The cold-producing medium that is transported to the 3rd row side heat-transfer pipe is flowing through after the 3rd row side heat-transfer pipe, in the outlet of the 3rd row side heat-transfer pipe by the 3rd Lie Nei branching portion branch to a two tertial heat-transfer pipe.The cold-producing medium that is transported to two tertial heat-transfer pipes is flowing through after two tertial heat-transfer pipes, from the outlet of two tertial heat-transfer pipes, is transported to the 3rd row side gas refrigerant pipe.
In this ceiling built-in air-conditioning system, during refrigeration, a part for cold-producing medium is delivered to secondary series side refrigerant pipe via secondary series side liquid refrigerant pipe, by in secondary series side heat-transfer pipe because carrying out heat exchange and be transported in the cold-producing medium branch of rich gas state the heat-transfer pipe of two secondary series with air, and the remainder of cold-producing medium is delivered to the 3rd row side refrigerant pipe via the 3rd row side liquid refrigerant pipe, to in the 3rd row side heat-transfer pipe, because carrying out heat exchange with air, in the cold-producing medium branch of rich gas state, be transported to two tertial heat-transfer pipes, therefore, the flow velocity that can suppress the cold-producing medium in rich gas state increases.In addition, in this ceiling built-in air-conditioning system, while heating, make in the heat-transfer pipe of two secondary series because of with air carry out in the cold-producing medium of heat exchange in rich solution state and two tertial heat-transfer pipes because carrying out the cold-producing medium interflow of heat exchange in rich solution state with air, and be delivered to secondary series side heat-transfer pipe, the 3rd row side heat-transfer pipe, therefore, can make the flow velocity of the cold-producing medium in rich solution state increase the pyroconductivity of secondary series side heat-transfer pipe, the 3rd row side heat-transfer pipe.In addition, in this ceiling built-in air-conditioning system, during refrigeration, making, in the stage of the liquid refrigerant pipe of cold-producing medium before flowing through the heat-transfer pipe of first row, cold-producing medium to be branched off into secondary series side liquid refrigerant pipe and the 3rd row side liquid refrigerant pipe.And, in this ceiling built-in air-conditioning system, cold-producing medium flows to the other end in the length direction one end from indoor heat converter, the length direction other end of indoor heat converter with branching portion in row in branch or interflow from the length direction other end of indoor heat converter, turn back mobile to the mode of one end.Therefore for the path of flow of refrigerant, be, the shorter path of round trip on the length direction of indoor heat converter only.
By this, in this ceiling built-in air-conditioning system, can, by utilizing branching portion in branching portion in secondary series, the 3rd row to make cold-producing medium flow branching suppress the increase of the pressure loss, therefore, can further improve the heat exchanger effectiveness of the indoor heat converter while freezing.Especially, in this ceiling built-in air-conditioning system, can suppress the increase of the flow velocity of the cold-producing medium in heat-transfer pipe and the tertial heat-transfer pipe of the secondary series that the cold-producing medium of the rich gas state larger on the impact of the pressure loss flows through, the heat exchanger effectiveness of the indoor heat converter in the time of therefore, effectively improving refrigeration.In addition, in this ceiling built-in air-conditioning system, make the flow velocity of the cold-producing medium in secondary series side heat-transfer pipe, the 3rd row side heat-transfer pipe that the cold-producing medium of the rich solution state less on the impact of the pressure loss flows through increase pyroconductivity, therefore, it is large that the degree of supercooling of refrigerant outlet during the heating of indoor heat converter easily becomes, thus the reduction of the heat exchanger effectiveness in the time of further suppressing to heat.In addition, in this ceiling built-in air-conditioning system, without for cold-producing medium being branched off into the heat-transfer pipe of secondary series and the branching portion of tertial heat-transfer pipe.And, in this ceiling built-in air-conditioning system, for the path of flow of refrigerant, it is the shorter path of round trip on the length direction of indoor heat converter only, thereby can suppress the increase of the pressure loss, therefore, the heat exchanger effectiveness of the indoor heat converter in the time of further improving refrigeration, in addition, the reduction of the heat exchanger effectiveness of the indoor heat converter in the time of can also further suppressing to heat.
The ceiling built-in air-conditioning system of the 15 invention is on the basis of the ceiling built-in air-conditioning system of the 14 invention, the bore of the 3rd row side liquid refrigerant pipe is than little at the bore of upside or the adjacent secondary series side liquid refrigerant pipe of downside, or the length of tube of the 3rd row side liquid refrigerant pipe is than long at the length of tube of upside or the adjacent secondary series side liquid refrigerant pipe of downside.
Therefore, in this ceiling built-in air-conditioning system, during refrigeration, easily there is more flow of refrigerant in the less secondary series side liquid refrigerant pipe of flow path resistance, therefore, compared with tertial heat-transfer pipe, have more flow of refrigerant in the heat-transfer pipe of secondary series.
By this, in this ceiling built-in air-conditioning system, it is large that the degree of superheat of the cold-producing medium that the refrigerant outlet during from the refrigeration of indoor heat converter flows out easily becomes, thus the heat exchanger effectiveness of the indoor heat converter in the time of further improving refrigeration.
Accompanying drawing explanation
Fig. 1 is the schematic configuration diagram having adopted as the aircondition of the indoor unit of the ceiling built-in air-conditioning system of an embodiment of the present invention.
Fig. 2 is the stereoscopic figure as the indoor unit of the ceiling built-in air-conditioning system of an embodiment of the present invention.
Fig. 3 is the schematic side sectional view as the indoor unit of the ceiling built-in air-conditioning system of an embodiment of the present invention, is the A-O-A cutaway view of Fig. 4.
Fig. 4 is the diagrammatic top view that has represented as the removal of the indoor unit of the ceiling built-in air-conditioning system of embodiment of the present invention the state after top board.
Fig. 5 is the figure representing as the refrigerant passage of the indoor heat converter in the indoor unit of the ceiling built-in air-conditioning system of the first embodiment.
Fig. 6 is the figure that represents the shape of U word portion.
Fig. 7 is the figure of the shape of branching portion between the row that represent in the first embodiment and variation 4 thereof.
Fig. 8 be represent as the variation 1 of the first embodiment the indoor unit of ceiling built-in air-conditioning system in the figure of refrigerant passage of indoor heat converter.
Fig. 9 is the figure of the shape of branching portion between the row that represent in the variation 1 of the first embodiment.
Figure 10 is the figure representing as the refrigerant passage of the indoor heat converter in the indoor unit of the ceiling built-in air-conditioning system of the variation 2 of the first embodiment.
Figure 11 is the figure of the shape of branching portion between the row that represent in the variation 2 of the first embodiment.
Figure 12 is the figure representing as the refrigerant passage of the indoor heat converter in the indoor unit of the ceiling built-in air-conditioning system of the variation 3 of the first embodiment.
Figure 13 is the figure of the shape of branching portion between the row that represent in the variation 3 of the first embodiment.
Figure 14 is the figure representing as the refrigerant passage of the indoor heat converter in the indoor unit of the ceiling built-in air-conditioning system of the variation 4 of the first embodiment.
Figure 15 is the figure representing as the refrigerant passage of the indoor heat converter in the indoor unit of the ceiling built-in air-conditioning system of the variation 5 of the first embodiment.
Figure 16 is the figure of the shape of branching portion between the row that represent in the variation 5 of the first embodiment.
Figure 17 is the figure representing as the refrigerant passage of the indoor heat converter in the indoor unit of the ceiling built-in air-conditioning system of the variation 6 of the first embodiment.
Figure 18 is the figure of the shape of branching portion between the row that represent in variation 6 and the variation 9 of the first embodiment.
Figure 19 is the figure representing as the refrigerant passage of the indoor heat converter in the indoor unit of the ceiling built-in air-conditioning system of the variation 7 of the first embodiment.
Figure 20 is the figure of the shape of branching portion between the row that represent in the variation 7 of the first embodiment.
Figure 21 is the figure representing as the refrigerant passage of the indoor heat converter in the indoor unit of the ceiling built-in air-conditioning system of the variation 8 of the first embodiment.
Figure 22 is the figure of the shape of branching portion between the row that represent in the variation 8 of the first embodiment.
Figure 23 is the figure representing as the refrigerant passage of the indoor heat converter in the indoor unit of the ceiling built-in air-conditioning system of the variation 9 of the first embodiment.
Figure 24 is the figure of the shape of branching portion between the row that represent in the variation 9 of the first embodiment.
Figure 25 is the figure representing as the refrigerant passage of the indoor heat converter in the indoor unit of the ceiling built-in air-conditioning system of the second embodiment.
Figure 26 is the figure of the shape of branching portion between the row that represent in the second embodiment.
Figure 27 is the figure representing as the refrigerant passage of the indoor heat converter in the indoor unit of the ceiling built-in air-conditioning system of the variation 1 of the second embodiment.
Figure 28 is the figure of the shape of branching portion between the row that represent in the variation 1 of the second embodiment.
Figure 29 is the figure representing as the refrigerant passage of the indoor heat converter in the indoor unit of the ceiling built-in air-conditioning system of the variation 2 of the second embodiment.
Figure 30 is the figure of the shape of branching portion between the row that represent in the variation 2 of the second embodiment.
Figure 31 is the figure representing as the refrigerant passage of the indoor heat converter in the indoor unit of the ceiling built-in air-conditioning system of the variation 3 of the second embodiment.
Figure 32 is the figure of the shape of branching portion between the row that represent in the variation 3 of the second embodiment.
Figure 33 is the figure representing as the refrigerant passage of the indoor heat converter in the indoor unit of the ceiling built-in air-conditioning system of the 3rd embodiment.
Figure 34 is the figure that represents the interior branching portion of secondary series of the 3rd embodiment and the shape of the interior branching portion of the 3rd row.
Figure 35 is the stereoscopic figure as the indoor unit of the ceiling built-in air-conditioning system of another embodiment of the present invention.
Figure 36 is the diagrammatic top view that has represented as the removal of the indoor unit of the ceiling built-in air-conditioning system of another embodiment of the present invention the state after top board.
Figure 37 is the stereoscopic figure as the indoor unit of the ceiling built-in air-conditioning system of another embodiment of the present invention.
Figure 38 is the diagrammatic top view that has represented as the removal of the indoor unit of the ceiling built-in air-conditioning system of another embodiment of the present invention the state after top board.
The specific embodiment
Below, with reference to the accompanying drawings the embodiment of ceiling built-in air-conditioning system of the present invention is described.
< basic structure >
Fig. 1 is the schematic configuration diagram having adopted as the aircondition 1 of the indoor unit 4 of the ceiling built-in air-conditioning system of an embodiment of the present invention.Aircondition 1 is split type aircondition, mainly has: outdoor unit 2; Indoor unit 4; And liquid refrigerant communicating pipe 5 and the gas refrigerant communicating pipe 6 of connection outdoor unit 2 and indoor unit 4, to form the refrigerant loop 10 of steam compression type.
It is outdoor etc. that outdoor unit 2 is arranged at, and mainly has compressor 21, four-way switching valve 22, outdoor heat converter 23, expansion valve 24, hydraulic fluid side stop valve 25 and gas side stop valve 26.
Compressor 21 is the compressors for discharge this high-pressure gas refrigerant after becoming high-pressure gas refrigerant low-pressure refrigerant gas is sucked, compressed.
Four-way switching valve 22 is the valves for switch the flow direction of cold-producing medium when switching refrigeration and heating.Four-way switching valve 22 can time link together the gas side of the discharge side of compressor 21 and outdoor heat converter 23 in refrigeration, and by the suction side of gas side stop valve 26 and compressor 21 link together (with reference to the solid line of the four-way switching valve 22 in Fig. 1).In addition, four-way switching valve 22 can link together the discharge side of compressor 21 and gas side stop valve 26 when heating, and the suction side of the gas side of outdoor heat converter 23 and compressor 21 is linked together (with reference to the dotted line of the four-way switching valve 22 in Fig. 1).
Outdoor heat converter 23 is the heat exchangers that work and work as the evaporimeter of cold-producing medium when heating as the condenser of cold-producing medium when refrigeration.The hydraulic fluid side of outdoor heat converter 23 is connected with expansion valve 24, and gas side is connected with four-way switching valve 22.
Expansion valve 24 is following electric expansion valves: when refrigeration, can be that the high pressure liquid refrigerant after being condensed in outdoor heat converter 23 is delivered to indoor heat converter 42 (aftermentioned) be front, this high pressure liquid refrigerant is reduced pressure, when heating, can, condensed high pressure liquid refrigerant in indoor heat converter 42 is delivered to before outdoor heat converter 23, this high pressure liquid refrigerant be reduced pressure.
Hydraulic fluid side stop valve 25 and gas side stop valve 26 are valves of being located at the connector being connected with outside equipment, pipe arrangement (specifically liquid refrigerant is communicated with pipe arrangement 5 and gas refrigerant connection pipe arrangement 6).Hydraulic fluid side stop valve 25 is connected with expansion valve 24.Gas side stop valve 26 is connected with four-way switching valve 22.
In addition, be provided with outdoor fan 27 in outdoor unit 2, this outdoor fan 27 is for outdoor air is sucked in unit, and is being expelled to outside unit after outdoor heat converter 23 supply chamber outer air.That is, outdoor heat converter 23 be using outdoor air as cooling source or heating source so that the heat exchanger of condensation of refrigerant, evaporation.
Indoor unit 4 is the ceiling built-in air-conditioning system that is called as the form of ceiling type in the present embodiment, has the housing 31 of receiving various constitution equipments in inside.Housing 31 consists of with the decoration panel 32 that is disposed at housing body 31a downside housing body 31a.As shown in Figure 3, housing body 31a is configured to be inserted in the upper opening forming of ceiling U of air conditioning chamber.In addition, decoration panel 32 is configured to embed the opening of ceiling U.At this, Fig. 2 is the stereoscopic figure as the indoor unit 4 of the ceiling built-in air-conditioning system of an embodiment of the present invention.Fig. 3 is the schematic side sectional view as the indoor unit 4 of the ceiling built-in air-conditioning system of an embodiment of the present invention, is the A-O-A cutaway view of Fig. 4.
As shown in Figures 3 and 4, housing body 31a is the roughly box-shaped body of octagonal lower surface opening that long limit and minor face are staggered to form overlooking while observing, and has: the staggered roughly octagonal top board 33 forming continuously of long limit and minor face; And the side plate 34 extending towards below from the circumference of top board 33.At this, Fig. 4 is the diagrammatic top view that has represented as the removal of the indoor unit 4 of the ceiling built-in air-conditioning system of embodiment of the present invention the state after top board 33.Side plate 34 forms by side plate 34a, the 34b on the long limit corresponding to top board 33,34c, 34d with corresponding to side plate 34e, 34f, 34g, the 34h of the minor face of top board 33.Side plate 34h forms for the part for indoor heat converter 42 and the hydraulic fluid side tube connector 51 linking together cold-producing medium communicating pipe 5,6 and gas side tube connector 61 are run through.
As shown in Figure 2, Figure 3 and Figure 4, decoration panel 32 is to overlook to be roughly tetragonal plate body, mainly the panel body 32a that is fixed on housing body 31a bottom, consists of.Substantial middle place at panel body 32a has: the suction inlet 35 that sucks the air in air conditioning chamber; And with overlooking the blow-off outlet 36 towards blow out air in air conditioning chamber that surrounds that mode around suction inlet 35 forms while observing.Suction inlet 35 is to be roughly tetragonal opening.In suction inlet 35, be provided with suction grid 37 and the filter 38 for the airborne dust sucking from suction inlet 35 is removed.Blow-off outlet 36 is the openings that are roughly four side ring shapes.In blow-off outlet 36, in the mode on the tetragonal each limit corresponding to panel body 32a, be provided with horizontal tail 39a, the 39b, 39c, the 39d that to blowing out, to the wind direction of the air in air conditioning chamber, regulate.
At the internal main of housing body 31a, to dispose indoor fan 41 and indoor heat converter 42, wherein, above-mentioned indoor fan 41 is as centrifugal blower, in suction inlet 35 suction casing main body 31a by the air in air conditioning chamber via decoration panel 32, and blow out in housing body 31a via the blow-off outlet 36 of decoration panel 32.
Indoor fan 41 has: the fan motor 41a that is located at the centre of the top board 33 of housing body 31a; And the impeller 41b that is connected and is driven in rotation with fan motor 41a.Impeller 41b is the impeller with turbo blade, can be from below towards the inside air amount of impeller 41b, and blow out towards the outer circumferential side of overlooking the impeller 41b while observing.
Indoor heat converter 42 is the fin tube type heat exchangers that are disposed at the outer circumferential side of overlooking the indoor fan 41 while observing.More specifically, indoor heat converter 42 is bent the surrounding being configured to indoor fan 41 and surrounds, it is to be called as the finned fin tube type heat exchanger of intersection, has the many heat-transfer pipes that arrange across many thermofins of predetermined distance configuration with to run through the state of these thermofins along thickness of slab direction.As mentioned above, the hydraulic fluid side of indoor heat converter 42 is connected with liquid refrigerant communicating pipe 5 via hydraulic fluid side tube connector 51, and the gas side of indoor heat converter 41 is connected with gas refrigerant communicating pipe 6 via gas side tube connector 61.In addition, indoor heat converter 42 works as the evaporimeter of cold-producing medium when refrigeration, and the condenser as cold-producing medium when heating works.By this, indoor heat converter 42 carries out heat exchange with the air blowing out from indoor fan 41, thus can be when refrigeration cooling-air, when heating, add hot-air.For structure, the feature of indoor heat converter 42, will in indoor heat converter >, the indoor heat converter > of < the second embodiment of < the first embodiment and the indoor heat converter > part of < the 3rd embodiment, be elaborated.
In addition, at the downside of indoor heat converter 42, dispose the drain pan 40 of the drain water producing for the moisture of admission of air is condensed in indoor heat converter 42.Drain pan 40 is installed on the bottom of housing body 31a.On drain pan 40, be formed with and blow out hole 40a, 40b, 40c, 40d, 40e, 40f, 40g, inlet hole 40h and sluicing receiving slit 40i.Blow out hole 40a, 40b, 40c, 40d, 40e, 40f, 40g is communicated with the blow-off outlet 36 of decoration panel 32.Inlet hole 40h is communicated with the suction inlet 35 of decoration panel 32.Sluicing receiving slit 40i is formed at the downside of indoor heat converter 42.In addition, in the inlet hole 40h of drain pan 40, dispose the horn mouth 41c for the air sucking from suction inlet 35 being guided to the impeller 41b of indoor fan.
< elemental motion >
Then, cooling operation and the action that heats the aircondition 1 in running are described.
In refrigerant loop 10 when refrigeration, the state shown in the solid line of four-way switching valve 22 in Fig. 1.In addition, hydraulic fluid side stop valve 25, gas side stop valve 26 are in open mode, and expansion valve 24 carries out regulation so that cold-producing medium is reduced pressure.
In the state of this refrigerant loop 10, the gas refrigerant of low pressure is inhaled in compressor 21, compressed and become the gas refrigerant of high pressure in compressor 21, and discharges from compressor 21.The gas refrigerant of this high pressure is transported to outdoor heat converter 23 via four-way switching valve 22, and in outdoor heat converter 23, carries out heat exchange with outdoor air and condensation becomes the liquid refrigerant of high pressure.The liquid refrigerant of this high pressure is transported to expansion valve 24, and in expansion valve 24, is depressurized and becomes the cold-producing medium of the gas-liquid two-phase state of low pressure.The cold-producing medium of the gas-liquid two-phase state of this low pressure is transported to indoor heat converter 42 via hydraulic fluid side stop valve 25, liquid refrigerant communicating pipe 5 and hydraulic fluid side tube connector 51, in indoor heat converter 42, carries out heat exchange and evaporates the gas refrigerant that becomes low pressure with the air blowing out from indoor fan 41.The gas refrigerant of this low pressure is delivered to compressor 21 again via gas side tube connector 61, gas refrigerant communicating pipe 6, gas side stop valve 26 and four-way switching valve 22.
Then, in the refrigerant loop 10 when heating, the state shown in the dotted line of four-way switching valve 22 in Fig. 1.In addition, hydraulic fluid side stop valve 25, gas side stop valve 26 are in open mode, and expansion valve 24 carries out regulation so that cold-producing medium is reduced pressure.
In the state of this refrigerant loop 10, the gas refrigerant of low pressure is inhaled in compressor 21, compressed and become the gas refrigerant of high pressure in compressor 21, and discharges from compressor 21.The gas refrigerant of this high pressure is transported to indoor heat converter 42 via four-way switching valve 22, gas side stop valve 26, gas refrigerant communicating pipe 6 and gas side tube connector 61, carries out heat exchange and condensation becomes the liquid refrigerant of high pressure in indoor heat converter 42 with the air that blows out from indoor fan 41.The liquid refrigerant of this high pressure is transported to expansion valve 24 via hydraulic fluid side tube connector 51, liquid refrigerant communicating pipe 5 and hydraulic fluid side stop valve 25, and decompression and become the cold-producing medium of the gas-liquid two-phase state of low pressure in expansion valve 24.The cold-producing medium of the gas-liquid two-phase state of this low pressure is transported to outdoor heat converter 23, in outdoor heat converter 23, carries out heat exchange and evaporates the gas refrigerant that becomes low pressure with outdoor air.The gas refrigerant of this low pressure is delivered to compressor 21 again via four-way switching valve 22.
The indoor heat converter > of < the first embodiment
(1) structure of indoor heat converter
As shown in Figures 3 and 4, the indoor heat converter 42 of the first embodiment adopts following structure: will at multiple heat- transfer pipes 71,72,73 of internal flow, be configured to multistage (multirow) on above-below direction for cold-producing medium, and in order to realize high performance, they are arranged to three row in the flow direction from the air that blows out as the indoor fan 41 of centrifugal blower.
More specifically, as shown in Fig. 3～Fig. 5, indoor heat converter 42 mainly has the first heat exchange department 42a, the second heat exchange department 42b and the 3rd heat exchange department 42c.At this, Fig. 5 is the figure representing as the refrigerant passage of the indoor heat converter 42 in the indoor unit 4 of the ceiling built-in air-conditioning system of the first embodiment.In Fig. 5, with solid line, represent to observe from arrow B direction the distolateral state of length direction one of indoor heat converter 42, and for the ease of diagram, with dashed line view, another distolateral state of length direction of observing indoor heat converter 42 from arrow C direction is shown overlappingly with one end side of indoor heat converter 42.
The first heat exchange department 42a forms in indoor heat converter 42 in the flow direction of air the row of weather side (following, to be made as first row).The first heat exchange department 42a has: across many first thermofins 81 of predetermined distance configuration; And many (being ten herein) first heat-transfer pipes 71 that arrange under the state that these first thermofins 81 are run through along thickness of slab direction.The first thermofin 81 is tabular members elongated on above-below direction.The first heat-transfer pipe 71 is the pipe components that extend on the length direction of indoor heat converter 42, and it is configured to ten sections on above-below direction.
The second heat exchange department 42b forms in indoor heat converter 42 row of secondary series in the flow direction of air.The second heat exchange department 42b has: across many second thermofins 82 of predetermined distance configuration; And many (being ten herein) second heat-transfer pipes 72 that arrange under the state that these second thermofins 82 are run through along thickness of slab direction.The second thermofin 82 is tabular members elongated on above-below direction.The second heat-transfer pipe 72 is the pipe components that extend on the length direction of indoor heat converter 42, and it is configured to ten sections on above-below direction.
The 3rd heat exchange department 42c forms in indoor heat converter 42 in the flow direction of air the row of downwind side (following, to be made as the 3rd row).The 3rd heat exchange department 42c has: across many 3rd thermofins 83 of predetermined distance configuration; And many (being ten herein) the 3rd heat-transfer pipes 73 that arrange under the state that these the 3rd thermofins 83 are run through along thickness of slab direction.The 3rd thermofin 83 is tabular members elongated on above-below direction.The 3rd heat-transfer pipe 73 is the pipe components that extend on the length direction of indoor heat converter 42, and it is configured to ten sections on above-below direction.
Indoor heat converter 42 is by making these heat exchange departments 42a, 42b, 42c overlapping and mode around the indoor fan 42 of overlooking while observing is bending to be formed to surround in the flow direction of air.At this, heat- transfer pipe 71,72,73 is configured to zigzag with respect to thermofin 81,82,83 entirety.
On hydraulic fluid side tube connector 51, be connected with current divider 52, this current divider 52 becomes the refrigerant inlet at the indoor heat converter 42 of when refrigeration indoor heat converter 42 working as the evaporimeter of cold-producing medium, in addition, also become the refrigerant outlet of when heating indoor heat converter 42 indoor heat converter 42 working as the condenser of cold-producing medium.On current divider 52, be connected with distolateral many (only illustrating three in Fig. 5) the liquid refrigerant pipes 91 that are connected with the first heat-transfer pipe 71 of indoor heat converter 42 of length direction one at indoor heat converter 42.At this, liquid refrigerant pipe 91 consists of capillary.
On gas side tube connector 61, be connected with header box 62, this header box 52 becomes the refrigerant outlet at the indoor heat converter 42 of when refrigeration indoor heat converter 42 working as the evaporimeter of cold-producing medium, in addition, also become the refrigerant inlet of when heating indoor heat converter 42 indoor heat converter 42 working as the condenser of cold-producing medium.On header box 62, be connected with distolateral many (only illustrating three in Fig. 5) the secondary series side gas refrigerant pipes 92 that are connected with the second heat-transfer pipe 72 of indoor heat converter 42 of length direction one at indoor heat converter 42 and distolateral many of being connected with the tertial heat-transfer pipe 72 of indoor heat converter 42 of length direction one (only illustrating three in Fig. 5) the 3rd row side gas refrigerant pipe 93 at indoor heat converter 42.
Indoor heat converter 42 has the refrigerant passage that multistage (only illustrating three sections in Fig. 5) forms by connecting the heat-transfer pipe 71,72,73 of two sections of three row.Each refrigerant passage has the first heat-transfer pipe 71a being connected with liquid refrigerant pipe 91 in the first heat-transfer pipe 71.The first heat-transfer pipe 71a the length direction of indoor heat converter 42 another distolateral via the U word 71c of portion be disposed at than first heat-transfer pipe 71 at the upside place of high one section of the first heat-transfer pipe 71a the first heat-transfer pipe 71b be connected.As shown in Figure 6, the 71c of U word portion is the U-shaped tube portion that the heat-transfer pipe (being herein the first heat-transfer pipe 71) being configured in same row is connected.The first heat-transfer pipe 71b the length direction one of indoor heat converter 42 distolateral with row between branching portion 71d be connected.Between row, branching portion 71d will flow through the part that the cold-producing medium after the first heat-transfer pipe 71b is divided into two when freezing.Between row one side of the branch of branching portion 71d distolateral the second heat-transfer pipe 72 with being disposed at the first heat-transfer pipe 71b upside in the second heat-transfer pipe 72 of the length direction one of indoor heat converter 42 the second heat-transfer pipe 72a be connected.Between row the opposite side of the branch of branching portion 71 distolateral the 3rd heat-transfer pipe 73 with being disposed at the second heat-transfer pipe 72a downside in the 3rd heat-transfer pipe 73 of the length direction one of indoor heat converter 42 the 3rd heat-transfer pipe 73a be connected.As shown in Figure 7, between row, branching portion 71d is at the pars intermedia of the U-shaped tube portion that the second heat-transfer pipe 72 and the 3rd heat-transfer pipe 73 are linked together to be connected with from the tube portion of the shape of the end of the extended U-shaped tube portion of the first heat-transfer pipe 71.At this, since the extended U-shaped tube portion of the first heat-transfer pipe 71, be set to since the flow path length of the second heat-transfer pipe 72 with identical from the flow path length of the 3rd heat-transfer pipe 73 with the link position between the U-shaped tube portion that the second heat-transfer pipe 72 and the 3rd heat-transfer pipe 73 are linked together.The second heat-transfer pipe 72a the length direction of indoor heat converter 42 another distolateral via the U word 72c of portion (with reference to Fig. 6) be disposed at than second heat-transfer pipe 72 at the downside place of low one section of the second heat-transfer pipe 72a the second heat-transfer pipe 72b be connected.The 3rd heat-transfer pipe 73a the length direction of indoor heat converter 42 another distolateral via the U word 73c of portion (with reference to Fig. 6) be disposed at than the 3rd heat-transfer pipe 73 at the downside place of low one section of the 3rd heat-transfer pipe 73a the 3rd heat-transfer pipe 73b be connected.The second heat-transfer pipe 72b is connected with secondary series side gas refrigerant pipe 92 the length direction one of indoor heat converter 42 is distolateral.The 3rd heat-transfer pipe 73b is connected with the 3rd row side gas refrigerant pipe 93 the length direction one of indoor heat converter 42 is distolateral.At this, heat-transfer pipe 71a, 71b are constituted as a heat-transfer pipe that bends to hairpin that comprises the U word 71c of portion.In addition, heat-transfer pipe 72a, 72b are constituted as a heat-transfer pipe that bends to hairpin that comprises the U word 72c of portion.In addition, heat-transfer pipe 73a, 73b are constituted as a heat-transfer pipe that bends to hairpin that comprises the U word 73c of portion.
By this, in the indoor heat converter 42 of present embodiment, working as the evaporimeter of cold-producing medium in the case of in when refrigeration, the hydraulic fluid side tube connector 51 of the refrigerant inlet when as refrigeration and current divider 52 and flow through a heat-transfer pipe the first heat-transfer pipe 71a (the first upstream side heat-transfer pipe) in the first heat-transfer pipe 71 that cold-producing medium after liquid refrigerant pipe 91 is transported to first row.The cold-producing medium that is transported to the first heat-transfer pipe 71a is flowing through after the first heat-transfer pipe 71a, also flows through the first i.e. the first heat-transfer pipe 71b (the first downstream heat-transfer pipe) of heat-transfer pipe 71 of the first row different from the first heat-transfer pipe 71a.Flow through cold-producing medium after the first heat-transfer pipe 71b the outlet of the first heat-transfer pipe 71b be listed as a branching portion 71d and be branched off into a heat-transfer pipe in the second heat-transfer pipe 72 of secondary series a heat-transfer pipe in the second heat-transfer pipe 72a (the second upstream side heat-transfer pipe) and tertial the 3rd heat-transfer pipe 73 be the 3rd heat-transfer pipe 73a (the 3rd upstream side heat-transfer pipe).In addition, the cold-producing medium that is transported to the second heat-transfer pipe 72a is flowing through after the second heat-transfer pipe 72a, also flow through the second i.e. the second heat-transfer pipe 72b (the second downstream heat-transfer pipe) of heat-transfer pipe 72 of the secondary series different from the second heat-transfer pipe 72a, and be transported to secondary series side gas refrigerant pipe 92 from the outlet of the second heat-transfer pipe 72b.In addition, the cold-producing medium that is transported to the 3rd heat-transfer pipe 73a is flowing through after the 3rd heat-transfer pipe 73a, also flow through the tertial three heat-transfer pipe 73 i.e. three heat-transfer pipe 73b (three downstream heat-transfer pipe) different from the 3rd heat-transfer pipe 73a, and be transported to the 3rd row side gas refrigerant pipe 93 from the outlet of the 3rd heat-transfer pipe 73b.Header box 62 and the gas side tube connector 61 of the refrigerant outlet when flowing through cold-producing medium after secondary series side gas refrigerant pipe 92 and the 3rd row side gas refrigerant pipe 93 and being transported to as refrigeration.
In addition, in the indoor heat converter 42 of present embodiment, working as the condenser of cold-producing medium when heating, via the gas side tube connector 61 of the refrigerant inlet when heating and header box 62 and flow through a heat-transfer pipe the second heat-transfer pipe 72b in the second heat-transfer pipe 72 that cold-producing medium after secondary series side gas refrigerant pipe 92 and the 3rd row side gas refrigerant pipe 93 is transported to secondary series and a heat-transfer pipe the 3rd heat-transfer pipe 73b in tertial the 3rd heat-transfer pipe 73.The cold-producing medium that is transported to the second heat-transfer pipe 72b is flowing through after the second heat-transfer pipe 72b, also flows through the second i.e. the second heat-transfer pipe 72a of heat-transfer pipe 72 of the secondary series different from the second heat-transfer pipe 72b.The cold-producing medium that is transported to the 3rd heat-transfer pipe 73b is flowing through after the 3rd heat-transfer pipe 73b, also flows through the tertial three heat-transfer pipe 73 i.e. three heat-transfer pipe 73a different from the 3rd heat-transfer pipe 73b.Flow through the cold-producing medium of the second heat-transfer pipe 72a and flow through between the cold-producing medium utilization row of the 3rd heat-transfer pipe 73a branching portion 71d at the outlet of the second heat-transfer pipe 72a and the outlet of the 3rd heat-transfer pipe 73a interflow, and be transported to i.e. the first heat-transfer pipe 71b of a heat-transfer pipe in the first heat-transfer pipe 71 of first row.In addition, the cold-producing medium that is transported to the first heat-transfer pipe 71b is flowing through after the first heat-transfer pipe 71b, also flows through the first i.e. the first heat-transfer pipe 71a of heat-transfer pipe 71 of the first row different from the first heat-transfer pipe 71b, and is transported to liquid refrigerant pipe 91.Flow through current divider 52 and hydraulic fluid side tube connector 51 that cold-producing medium after liquid refrigerant pipe 91 is transported to the refrigerant outlet when heating.
(2) there is the feature of the indoor unit of indoor heat converter
As having in the indoor unit 4 of ceiling built-in air-conditioning system of indoor heat converter 42 of present embodiment, there is following feature.
(A)
The indoor heat converter 42 of present embodiment has following structure: the refrigerant inlet at the indoor heat converter 42 of when refrigeration indoor heat converter 42 working as the evaporimeter of cold-producing medium is connected with many liquid refrigerant pipes 91, and these many liquid refrigerant pipes 91 are connected with the heat-transfer pipe 71 that the row of weather side in the flow direction of air are first row.In addition, this indoor heat converter 42 has following structure: when refrigeration, the refrigerant outlet of indoor heat converter 42 is connected with many gas refrigerant pipes 92,93, and the part in these many gas refrigerant pipes 92,93 is that secondary series side gas refrigerant pipe 92 is connected with the heat-transfer pipe 72 of secondary series in the flow direction of air.In addition, this indoor heat converter 42 has following structure: the remainder in many gas refrigerant pipes 92,93 i.e. the 3rd row side gas refrigerant pipe 93 is that tertial heat-transfer pipe 73 is connected with the row of downwind side in the flow direction of air.
Therefore, in the indoor unit 4 of present embodiment, during refrigeration, a part for the cold-producing medium that refrigerant inlet during from the refrigeration of indoor heat converter 42 flows into, just having carried out heat exchange with the air of the temperature heat-transfer pipe that passes across secondary series 72 higher than the temperature of air that passes across tertial heat-transfer pipe 73, is just transported to secondary series side gas refrigerant pipe 92.In addition, in this indoor unit 4, during refrigeration, the remainder of the cold-producing medium that the refrigerant inlet during from the refrigeration of indoor heat converter 42 flows into, just having carried out heat exchange with the air that passes across tertial heat-transfer pipe 73, is just transported to the 3rd row side gas refrigerant pipe 93.In addition, flow through cold-producing medium after secondary series side gas refrigerant pipe 92 and the cold-producing medium interflow of flowing through after the 3rd row side gas refrigerant pipe 93, and the refrigerant outlet during from the refrigeration of indoor heat converter 42 flows out.At this, because the degree of superheat of just having carried out the cold-producing medium after heat exchange with the air of heat-transfer pipe 72 that passes across secondary series is subject to the temperature impact of the air of the heat-transfer pipe 72 that passes across secondary series, therefore easily than just and the air that passes across tertial heat-transfer pipe 73 to have carried out the degree of superheat of the cold-producing medium after heat exchange large.
By this, in this indoor unit 4, the degree of superheat of the cold-producing medium that the refrigerant outlet during from the refrigeration of indoor heat converter 42 flows out is all compared easy increase with the structure that tertial heat-transfer pipe 73 is connected by all gas refrigerant pipes 92,93 with adopting, thereby can improve the heat exchanger effectiveness while freezing.
In addition, in this indoor unit 4, while heating, the cold-producing medium that the refrigerant inlet during from the heating of indoor heat converter 42 flows into be all just and the air of the minimum heat-transfer pipe that passes across first row 71 of temperature be just transported to liquid refrigerant pipe 91 having carried out heat exchange.
By this, in this indoor unit 4, the degree of supercooling of refrigerant outlet during the heating of indoor heat converter 42 is difficult for diminishing, thus the reduction of the heat exchanger effectiveness in the time of heating.
As mentioned above, in this indoor unit 4, the degree of supercooling of the refrigerant outlet while making the heating of indoor heat converter 42 is difficult for reducing, and the degree of superheat of the cold-producing medium that flows out of the refrigerant outlet while making the refrigeration from indoor heat converter 42 easily increases, thereby the reduction of the heat exchanger effectiveness of the indoor heat converter 42 in the time of heating, and can improve the heat exchanger effectiveness of the indoor heat converter 42 in when refrigeration.
(B)
In the indoor heat converter 42 of present embodiment, liquid refrigerant pipe 91, secondary series side gas refrigerant pipe 92 and the 3rd row side gas refrigerant pipe 93 connect with length direction one end of corresponding heat- transfer pipe 71,72,73.
By this, in the indoor unit 4 of present embodiment, can be integrated into that the length direction one of indoor heat converter 42 is distolateral carries out the connection operation towards heat- transfer pipe 71,72,73 of liquid refrigerant pipe 91, secondary series side gas refrigerant pipe 92 and the 3rd row side gas refrigerant pipe 93, therefore can improve the assembleability of indoor heat converter 42.
And in the indoor heat converter 42 of present embodiment, in each biographies heat pipe 71,72,73, mobile cold-producing medium to turn back to the mode of one end and to flow from the length direction other end from length direction one end of indoor heat converter 42 flows to the other end.Therefore, it is distolateral that not only liquid refrigerant pipe 91, secondary series side gas refrigerant pipe 92 and the 3rd row side gas refrigerant pipe 93 are integrated into the length direction one of indoor heat converter 42, and it is distolateral that between row, branching portion 71d is also disposed at the length direction one of indoor heat converter 42.
By this, in the indoor unit 4 of present embodiment, in the case of adopting when branching portion 71d between assembling need be listed as during indoor heat converter 42 is towards the structure of the connection operations such as the soldering of heat- transfer pipe 71,72,73, can be integrated into the distolateral branching portion 71d that carries out between liquid refrigerant pipe 91, secondary series side gas refrigerant pipe 92, the 3rd row side gas refrigerant pipe 93 and row of the length direction one of indoor heat converter 42 towards the connection operation of heat- transfer pipe 71,72,73, therefore, can further improve the assembleability of indoor heat converter 42.
(C)
The indoor heat converter 42 of present embodiment has in when refrigeration the cold-producing medium of outlet of the heat-transfer pipe 71 that is transported to first row is branched off into branching portion 71d between the heat-transfer pipe 72 of secondary series and the row of tertial heat-transfer pipe 73.In addition in the outlet of the heat-transfer pipe 72 of the secondary series of when refrigeration indoor heat converter 42 working as the evaporimeter of cold-producing medium, be connected with secondary series side gas refrigerant pipe 92.In addition, in the outlet of the tertial heat-transfer pipe 73 of when refrigeration indoor heat converter 42 working as the evaporimeter of cold-producing medium, be connected with the 3rd row side gas refrigerant pipe 93.
In this indoor heat converter 42, during refrigeration, to in the heat-transfer pipe of first row 71, because carrying out heat exchange with air, in the cold-producing medium branch of rich gas (Japanese: ガ ス リ Star チ) state, be transported to heat-transfer pipe 72 and the tertial heat-transfer pipe 73 of secondary series, therefore, can suppress the flow velocity increase of the cold-producing medium in rich gas state.In addition, in this indoor heat converter 42, while heating, make in the heat-transfer pipe 72 of secondary series because of with air carry out in the cold-producing medium of heat exchange in rich solution (Japanese: liquid リ Star チ) state and tertial heat-transfer pipe 73 because carrying out the cold-producing medium interflow of heat exchange in rich solution state with air, and be delivered to the heat-transfer pipe 71 of first row, therefore, can make the flow velocity of the cold-producing medium in rich solution state increase the pyroconductivity of the heat-transfer pipe 71 of first row.
By this, in the indoor unit 4 of present embodiment, between being listed as by utilization, branching portion 71d makes cold-producing medium flow branching suppress the increase of the pressure loss, therefore, can further improve the heat exchanger effectiveness of the indoor heat converter 42 while freezing.Especially, in this indoor unit 4, the flow velocity that can suppress the cold-producing medium in heat-transfer pipe 72 and the tertial heat-transfer pipe 73 of the secondary series that the cold-producing medium of the rich gas state larger on the impact of the pressure loss flows through increases, the heat exchanger effectiveness of the indoor heat converter 42 in the time of therefore, effectively improving refrigeration.In addition, in this indoor unit 4, make the flow velocity of the cold-producing medium in the heat-transfer pipe 71 of the first row that the cold-producing medium of the rich solution state less on the impact of the pressure loss flows through increase pyroconductivity, therefore, it is large that the degree of supercooling of refrigerant outlet during the heating of indoor heat converter 42 easily becomes, thus the reduction of the heat exchanger effectiveness in the time of further suppressing to heat.
(D)
In the indoor heat converter 42 of present embodiment, be disposed at the upside place of high one section of the first heat-transfer pipe 71a (the first upstream side heat-transfer pipe) of being connected and being connected with liquid refrigerant pipe 91 than the upstream side of the first heat-transfer pipe 71b when freezing with the first heat-transfer pipe 71b (the first downstream heat-transfer pipe) of being connected of branching portion 71d between row.
In this indoor heat converter 42, while heating, the cold-producing medium that flows through the first heat- transfer pipe 71a, 71b flows in the mode declining towards liquid refrigerant pipe 91.
By this, in the indoor unit 4 of present embodiment, it is large that the degree of supercooling of refrigerant outlet during the heating of indoor heat converter 42 easily becomes, thus the reduction of the heat exchanger effectiveness in the time of further suppressing to heat.
(3) variation 1
Forming in the indoor heat converter 42 (with reference to Fig. 5) of above-mentioned indoor unit 4, between row, branching portion 71d links together with the second heat-transfer pipe 72a (the second upstream side heat-transfer pipe) and the 3rd heat-transfer pipe 73a (the 3rd upstream side heat-transfer pipe) that is disposed at the downside of the second heat-transfer pipe 72a the length direction one of indoor heat converter 42 is distolateral.
On the other hand, in the indoor heat converter 42 of indoor unit 4 that forms this variation, as shown in Fig. 8, Fig. 6 and Fig. 9, the second heat-transfer pipe 72a (the second upstream side heat-transfer pipe) that connects branching portion 71d between row is disposed to the downside that connects the 3rd heat-transfer pipe 73a (the 3rd upstream side heat-transfer pipe) of branching portion 71d between row.
Therefore,, in this indoor heat converter 42, when refrigeration, because making cold-producing medium, the effect of gravity more easily flows in large quantities the second heat-transfer pipe 72a compared with the 3rd heat-transfer pipe 73a.
By this, in the indoor unit 4 of this variation, it is large that the degree of superheat of the cold-producing medium that the refrigerant outlet during from the refrigeration of indoor heat converter 42 flows out easily becomes, thus the heat exchanger effectiveness of the indoor heat converter 42 in the time of further improving refrigeration.
(4) variation 2
Forming in the indoor heat converter 42 (with reference to Fig. 5) of above-mentioned indoor unit 4, between row, branching portion 71d is formed as: when refrigeration, the flow path length from the flow path length entrance that export to second heat-transfer pipe 72a (second upstream side heat-transfer pipe) of first heat-transfer pipe 72b (first downstream heat-transfer pipe) till and the entrance that export to three heat-transfer pipe 73a (three upstream side heat-transfer pipe) from first heat-transfer pipe 72b till of indoor heat converter 42 working as the evaporimeter of cold-producing medium is identical.
On the other hand, in the indoor heat converter 42 of indoor unit 4 that forms this variation, as Figure 10, shown in Fig. 6 and Figure 11, using between row, branching portion 71d is formed as: indoor heat converter 42 flow path length till the entrance that exports to the second heat-transfer pipe 72a (the second upstream side heat-transfer pipe) of the first heat-transfer pipe 71b (the first downstream heat-transfer pipe) as the evaporimeter of cold-producing medium works when refrigeration of the flow path length ratio till the entrance that exports to the 3rd heat-transfer pipe 73a (the 3rd upstream side heat-transfer pipe) of the first heat-transfer pipe 71b (the first downstream heat-transfer pipe) is long.More specifically, in this variation, as shown in figure 11, branching portion 71d between row is formed as being at the pars intermedia of the U-shaped tube portion that the first heat-transfer pipe 71 and the second heat-transfer pipe 72 are linked together and is connected with from the tube portion of the shape of the end of the extended U-shaped tube portion of the 3rd heat-transfer pipe 73.
Therefore,, in this indoor heat converter 42, during refrigeration, easily there is more flow of refrigerant till arrive via branching portion 71d between row from the outlet of the first heat-transfer pipe 71b the second heat-transfer pipe 72a that the flow path resistance of entrance is less.
By this, in the indoor unit 4 of this variation, it is large that the degree of superheat of the cold-producing medium that the refrigerant outlet during from the refrigeration of indoor heat converter 42 flows out easily becomes, thus the heat exchanger effectiveness of the indoor heat converter 42 in the time of further improving refrigeration.
(5) variation 3
Also can be used forming the feature of combined deformation example 1 and the feature of variation 2 in the indoor heat converter 42 (with reference to Fig. 5) of above-mentioned indoor unit 4.
; in the indoor heat converter 42 of indoor unit 4 that forms this variation; as shown in Figure 12, Fig. 6 and Figure 13; identical with variation 1, the second heat-transfer pipe 72a (the second upstream side heat-transfer pipe) that connects branching portion 71d between row is disposed to the downside that connects the 3rd heat-transfer pipe 73a (the 3rd upstream side heat-transfer pipe) of branching portion 71d between row.And, in the indoor heat converter 42 of indoor unit 4 that forms this variation, identical with variation 2, using between row, branching portion 71d is formed as: indoor heat converter 42 flow path length till the entrance that exports to the second heat-transfer pipe 72a (the second upstream side heat-transfer pipe) of the first heat-transfer pipe 71b (the first downstream heat-transfer pipe) as the evaporimeter of cold-producing medium works when refrigeration of the flow path length ratio till the entrance that exports to the 3rd heat-transfer pipe 73a (the 3rd upstream side heat-transfer pipe) of the first heat-transfer pipe 71b (the first downstream heat-transfer pipe) is long.
By this, in the indoor unit 4 of this variation, can obtain these two effects of the action effect of variation 1 and the action effect of variation 2.
(6) variation 4
Forming in the indoor heat converter 42 (with reference to Fig. 5) of above-mentioned indoor unit 4, the second heat-transfer pipe 72b (the second downstream heat-transfer pipe) being connected with secondary series side gas refrigerant pipe 92 is disposed at the downside place of low one section of the second heat-transfer pipe 72a (the second upstream side heat-transfer pipe) that the upstream side of the second heat-transfer pipe 72b when with refrigeration is connected.In addition, forming in the indoor heat converter 42 (with reference to Fig. 5) of above-mentioned indoor unit 4, the 3rd heat-transfer pipe 73b (the 3rd downstream heat-transfer pipe) being connected with the 3rd row side gas refrigerant pipe 93 is disposed at the downside place of low one section of the 3rd heat-transfer pipe 73a (the 3rd upstream side heat-transfer pipe) that the upstream side of the 3rd heat-transfer pipe 73b when with refrigeration is connected.
On the other hand, in the indoor heat converter 42 of indoor unit 4 that forms this variation, as shown in Figure 14, Fig. 6 and Fig. 7, the second heat-transfer pipe 72b (the second downstream heat-transfer pipe) being connected with secondary series side gas refrigerant pipe 92 is disposed at than the upside place of high one section of the second heat-transfer pipe 72a (the second upstream side heat-transfer pipe) being connected with the upstream side of the second heat-transfer pipe 72b in when refrigeration.In addition, forming in the indoor heat converter 42 (with reference to Fig. 5) of above-mentioned indoor unit 4, the 3rd heat-transfer pipe 73b (the 3rd downstream heat-transfer pipe) being connected is disposed to the upside place of high one section of the 3rd heat-transfer pipe 73a (the 3rd upstream side heat-transfer pipe) that the upstream side of the 3rd heat-transfer pipe 73b when with refrigeration is connected with the 3rd row side gas refrigerant pipe 93.
Therefore, in this indoor heat converter 42, during refrigeration, the cold-producing medium that flows through the second heat- transfer pipe 72a, 72b flows in the mode rising smoothly towards secondary series side gas refrigerant pipe 92, in addition, the cold-producing medium that flows through the 3rd heat- transfer pipe 73a, 73b is to flow towards the smooth mode rising of the 3rd row side gas refrigerant pipe 93.
By this, in the indoor unit 4 of this variation, the increase of the pressure loss in the time of suppressing cold-producing medium and flow through the second heat- transfer pipe 72a, 72b, in addition, the increase of the pressure loss in the time of can also suppressing cold-producing medium and flow through the 3rd heat- transfer pipe 73a, 73b, the heat exchanger effectiveness of the indoor heat converter 42 in the time of therefore, further improving refrigeration.
In this variation, the second heat-transfer pipe 72b is disposed to the upside of the second heat-transfer pipe 72a, and the 3rd heat-transfer pipe 73b is disposed to the upside of the 3rd heat-transfer pipe 73a, but also can only the second heat-transfer pipe 72b be disposed to the upside of the second heat-transfer pipe 72a, or only the 3rd heat-transfer pipe 73b be disposed to the upside of the 3rd heat-transfer pipe 73a.
(7) variation 5
Forming in the indoor heat converter 42 (with reference to Figure 14) of indoor unit 4 of variation 4, be disposed at the downside place of low one section of the first heat-transfer pipe 71a (the first upstream side heat-transfer pipe) of being connected and being connected with liquid refrigerant pipe 91 than the upstream side of the first heat-transfer pipe 71b when freezing with the first heat-transfer pipe 71b (the first downstream heat-transfer pipe) that between row, branching portion 71d is connected.
On the other hand, in the indoor heat converter 42 of indoor unit 4 that forms this variation, as shown in Figure 15, Fig. 6 and Figure 16, by with row between the first heat-transfer pipe 71b (the first downstream heat-transfer pipe) of being connected of branching portion 71d be disposed at the upside place of high one section of the first heat-transfer pipe 71a (the first upstream side heat-transfer pipe) of being connected and being connected with liquid refrigerant pipe 91 than the upstream side of the second heat-transfer pipe 71b when freezing.
Therefore, in this indoor heat converter 42, identical with the indoor heat converter 42 (with reference to Fig. 5) that forms above-mentioned indoor unit 4, when heating, the cold-producing medium that flows through the first heat- transfer pipe 71a, 71b flows in the mode declining towards liquid refrigerant pipe 91.
By this, in the indoor unit 4 of this variation, the degree of supercooling of refrigerant outlet during the heating of indoor heat converter 42 easily becomes larger than the degree of supercooling of variation 4, thus the reduction of the heat exchanger effectiveness in the time of further suppressing to heat.
(8) variation 6
Forming in the indoor heat converter (with reference to Figure 15) of indoor unit 4 of variation 5, between row, branching portion 71d links together with the second heat-transfer pipe 72a (the second upstream side heat-transfer pipe) and the 3rd heat-transfer pipe 73a (the 3rd upstream side heat-transfer pipe) that is disposed at the downside of the second heat-transfer pipe 72a the length direction one of indoor heat converter 42 is distolateral.
On the other hand, in the indoor heat converter 42 of indoor unit 4 that forms this variation, identical with the indoor heat converter 42 (with reference to Fig. 8) of indoor unit 4 that forms variation 1, as shown in Figure 17, Fig. 6 and Figure 18, the second heat-transfer pipe 72a (the second upstream side heat-transfer pipe) that connects branching portion 71d between row is disposed to the downside that connects the 3rd heat-transfer pipe 73a (the 3rd upstream side heat-transfer pipe) of branching portion 71d between row.
Therefore,, in this indoor heat converter 42, when refrigeration, because making cold-producing medium, the effect of gravity more easily flows in large quantities the 3rd heat-transfer pipe 73a compared with the second heat-transfer pipe 72a.
By this, in the indoor unit 4 of this variation, it is large that the degree of superheat of the cold-producing medium that the refrigerant outlet during from the refrigeration of indoor heat converter 42 flows out easily becomes, thus the heat exchanger effectiveness of the indoor heat converter 42 in the time of further improving refrigeration.
(9) variation 7
Forming in the indoor heat converter (with reference to Figure 15) of indoor unit 4 of variation 5, between row, branching portion 71d is formed as: when refrigeration, the flow path length from the flow path length entrance that export to second heat-transfer pipe 72a (second upstream side heat-transfer pipe) of first heat-transfer pipe 72b (first downstream heat-transfer pipe) till and the entrance that export to three heat-transfer pipe 73a (three upstream side heat-transfer pipe) from first heat-transfer pipe 72b till of indoor heat converter 42 working as the evaporimeter of cold-producing medium is identical.
On the other hand, in the indoor heat converter 42 of indoor unit 4 that forms this variation, identical with the indoor heat converter 42 (with reference to Figure 10) of indoor unit 4 that forms variation 2, as Figure 19, shown in Fig. 6 and Figure 20, using between row, branching portion 71d is formed as: indoor heat converter 42 flow path length till the entrance that exports to the second heat-transfer pipe 72a (the second upstream side heat-transfer pipe) of the first heat-transfer pipe 71b (the first downstream heat-transfer pipe) as the evaporimeter of cold-producing medium works when refrigeration of the flow path length ratio till the entrance that exports to the 3rd heat-transfer pipe 73a (the 3rd upstream side heat-transfer pipe) of the first heat-transfer pipe 71b (the first downstream heat-transfer pipe) is long.More specifically, in this variation, as shown in figure 20, branching portion 71d between row is formed as being at the pars intermedia of the U-shaped tube portion that the first heat-transfer pipe 71 and the second heat-transfer pipe 72 are linked together and is connected with from the tube portion of the shape of the end of the extended U-shaped tube portion of the 3rd heat-transfer pipe 73.
Therefore,, in this indoor heat converter 42, during refrigeration, easily there is more flow of refrigerant till arrive via branching portion 71d between row from the outlet of the first heat-transfer pipe 71b the second heat-transfer pipe 72a that the flow path resistance of entrance is less.
By this, in the indoor unit 4 of this variation, it is large that the degree of superheat of the cold-producing medium that the refrigerant outlet during from the refrigeration of indoor heat converter 42 flows out easily becomes, thus the heat exchanger effectiveness of the indoor heat converter 42 in the time of further improving refrigeration.
(10) variation 8
Also can be in the indoor heat converter 42 (with reference to Figure 15) of indoor unit 4 that forms variation 5 feature of combined deformation example 6 and the feature of variation 7 used.
; in the indoor heat converter 42 of indoor unit 4 that forms this variation; as shown in Figure 21, Fig. 6 and Figure 22; identical with variation 6, the second heat-transfer pipe 72a (the second upstream side heat-transfer pipe) that connects branching portion 71d between row is disposed to the downside that connects the 3rd heat-transfer pipe 73a (the 3rd upstream side heat-transfer pipe) of branching portion 71d between row.And, in the indoor heat converter 42 of indoor unit 4 that forms this variation, identical with variation 7, using between row, branching portion 71d is formed as: indoor heat converter 42 flow path length till the entrance that exports to the second heat-transfer pipe 72a (the second upstream side heat-transfer pipe) of the first heat-transfer pipe 71b (the first downstream heat-transfer pipe) as the evaporimeter of cold-producing medium works when refrigeration of the flow path length ratio till the entrance that exports to the 3rd heat-transfer pipe 73a (the 3rd upstream side heat-transfer pipe) of the first heat-transfer pipe 71b (the first downstream heat-transfer pipe) is long.
By this, in the indoor unit 4 of this variation, can obtain these two effects of the action effect of variation 1 and the action effect of variation 2.
(11) variation 9
The indoor heat converter 42 (with reference to Fig. 5) that forms above-mentioned indoor unit 4 has the refrigerant passage that multistage (only illustrating three sections in Fig. 5) forms by connecting the heat-transfer pipe 71,72,73 of two sections of three row, and the path that liquid refrigerant pipe 91 and gas refrigerant pipe 92,93 connected of these refrigerant passage is identical.Therefore, in the outlet of the outlet of the second heat-transfer pipe 72b (second downstream heat-transfer pipe) that with secondary series side gas refrigerant pipe 92 be connected of when refrigeration indoor heat converter 42 working as the evaporimeter of cold-producing medium and the 3rd heat-transfer pipe 73b (the 3rd downstream heat-transfer pipe) that is connected with the 3rd row side gas refrigerant pipe 93, be configured to away from the outlet of another second heat-transfer pipe 72b (the second downstream heat-transfer pipe) and the outlet of the 3rd heat-transfer pipe 73b (the 3rd downstream heat-transfer pipe) of formation refrigerant passage that is disposed at upside or downside.In addition at the entrance of the first heat-transfer pipe 71a that with liquid refrigerant pipe 91 be connected (first upstream side heat-transfer pipe) of when refrigeration indoor heat converter 24 working as the evaporimeter of cold-producing medium, be configured to away from the entrance of another first heat-transfer pipe 71a (the first upstream side heat-transfer pipe) that is disposed at upside or downside.
On the other hand, in the indoor heat converter 42 of indoor unit 4 that forms this variation, as shown in Figure 23, Fig. 6, Figure 18 and Figure 24, will be configured to adjacent with the outlet of another second heat-transfer pipe 72f (the second downstream heat-transfer pipe) and the outlet of the 3rd heat-transfer pipe 73f (the 3rd downstream heat-transfer pipe) that are disposed at upside or downside in the outlet of the second heat-transfer pipe 72b (second downstream heat-transfer pipe) of when refrigeration indoor heat converter 42 as the evaporimeter of cold-producing medium works and the outlet of the 3rd heat-transfer pipe 73b (the 3rd downstream heat-transfer pipe).In addition, adjacent using be configured to the entrance of another first heat-transfer pipe 71e (the first upstream side heat-transfer pipe) with being disposed at upside or downside at the entrance of the first heat-transfer pipe 71a (the first upstream side heat-transfer pipe) of when refrigeration indoor heat converter 24 as the evaporimeter of cold-producing medium works.
Particularly, the indoor heat converter 42 of this variation has multistage (only illustrating three sections in Figure 23) alternately by connect the heat-transfer pipe of two sections of three row the first refrigerant passage forming and the second refrigerant path consisting of the heat-transfer pipe that is connected two sections of another three row.At this, the first refrigerant passage and the refrigerant passage identical (with reference to Figure 17 and Figure 18) of indoor heat converter 42 that forms variation 6.Second refrigerant path has and in the first heat-transfer pipe 71, is connected with liquid refrigerant pipe 91 and is disposed at than the first heat-transfer pipe 71e at downside place of low one section of the first heat-transfer pipe 71a that forms the first refrigerant passage.The first heat-transfer pipe 71e the length direction of indoor heat converter 42 another distolateral via the U word 71c of portion (with reference to Fig. 6) be disposed at than first heat-transfer pipe 71 at the downside place of low one section of the first heat-transfer pipe 71e the first heat-transfer pipe 71f be connected.The first heat-transfer pipe 71f the length direction one of indoor heat converter 42 distolateral with row between branching portion 71d be connected.Between row, branching portion 71d will flow through the part that the cold-producing medium after the first heat-transfer pipe 71b is divided into two when freezing.Between row, one side of the branch of branching portion 71d is that the second heat-transfer pipe 72e is connected at the second heat-transfer pipe 72 of the distolateral upside with being disposed at the first heat-transfer pipe 71f in the second heat-transfer pipe 72 of length direction one of indoor heat converter 42.Between row, the opposite side of the branch of branching portion 71 is that the 3rd heat-transfer pipe 73e is connected at the 3rd heat-transfer pipe 73 of the distolateral upside with being disposed at the second heat-transfer pipe 72e in the 3rd heat-transfer pipe 73 of length direction one of indoor heat converter 42.As shown in figure 24, between row, branching portion 71d is at the pars intermedia of the U-shaped tube portion that the second heat-transfer pipe 72 and the 3rd heat-transfer pipe 73 are linked together to be connected with from the tube portion of the shape of the end of the extended U-shaped tube portion of the first heat-transfer pipe 71.At this, since the extended U-shaped tube portion of the first heat-transfer pipe 71, be set to since the flow path length of the second heat-transfer pipe 72 with identical from the flow path length of the 3rd heat-transfer pipe 73 with the link position between the U-shaped tube portion that the second heat-transfer pipe 72 and the 3rd heat-transfer pipe 73 are linked together.The second heat-transfer pipe 72e the length direction of indoor heat converter 42 another distolateral via the U word 72c of portion (with reference to Fig. 6) be disposed at than the downside place of low one section of the second heat-transfer pipe 72e and be disposed at than form the first refrigerant passage high one section of the second heat-transfer pipe 72b upside place the second heat-transfer pipe 72 the second heat-transfer pipe 72f be connected.The 3rd heat-transfer pipe 73e the length direction of indoor heat converter 42 another distolateral via the U word 73c of portion (with reference to Fig. 6) be disposed at than the downside place of low one section of the 3rd heat-transfer pipe 73e and be disposed at than form the first refrigerant passage high one section of the 3rd heat-transfer pipe 73b upside place the 3rd heat-transfer pipe 73 the 3rd heat-transfer pipe 73f be connected.The second heat-transfer pipe 72f is connected with secondary series side gas refrigerant pipe 92.The 3rd heat-transfer pipe 73b is connected with the 3rd row side gas refrigerant pipe 93.At this, heat-transfer pipe 71e, 71f are constituted as a heat-transfer pipe that bends to hairpin that comprises the U word 71c of portion.In addition, heat-transfer pipe 72e, 72f are constituted as a heat-transfer pipe that bends to hairpin that comprises the U word 72c of portion.In addition, heat-transfer pipe 73e, 73f are constituted as a heat-transfer pipe that bends to hairpin that comprises the U word 73c of portion.
Therefore, in this indoor heat converter 42, the second heat-transfer pipe 72b, the 72f (the second downstream heat-transfer pipe) that temperature uprises and the 3rd heat-transfer pipe 73b, 73f (the 3rd downstream heat-transfer pipe) centralized configuration are on thermofin 81,82,83, and the first heat-transfer pipe 71a, the 71e of temperature step-down (the first upstream side heat-transfer pipe) centralized configuration is on thermofin 81,82,83.In addition, in this indoor heat converter 42, during refrigeration, the high heat (Japanese: warm Hot) of the second heat-transfer pipe 72b, 72f (the second downstream heat-transfer pipe) and the 3rd heat-transfer pipe 73b, 73f (the 3rd downstream heat-transfer pipe) is difficult for being passed to via thermofin 81,82,83 other parts of thermofin 81,82,83, while heating, the heat of cooling (Japanese: cold Hot) of the first heat-transfer pipe 71a, 71e (the first upstream side heat-transfer pipe) is difficult for being passed to via thermofin 81,82,83 other parts of thermofin 81,82,83.
By this, in the indoor unit 4 of this variation, can do one's utmost to suppress because of the heat conduction via thermofin 81,82,83 produces while freezing and while heating indoor heat converter 42 heat exchanger effectiveness reduction.
The indoor heat converter > of < the second embodiment
(1) structure of indoor heat converter
The indoor heat converter 42 of present embodiment adopts following structure: identical with the indoor heat converter 42 of the first embodiment and variation thereof, as shown in Figures 3 and 4, to at multiple heat- transfer pipes 71,72,73 of internal flow, on above-below direction, be configured to multistage (multirow) for cold-producing medium, and in order to realize high performance, they are arranged to three row in the flow direction from the air that blows out as the indoor fan 41 of centrifugal blower.
As shown in figure 25, the indoor heat converter 42 of present embodiment is different in the structure of liquid refrigerant pipe 91, gas refrigerant pipe 92,93 and refrigerant passage from the indoor heat converter 42 of the first embodiment and variation thereof, but other structure is identical with the indoor heat converter 42 of the first embodiment and variation thereof, therefore, description thereof is omitted herein.
On hydraulic fluid side tube connector 51, be connected with current divider 52, this current divider 52 becomes the refrigerant inlet at the indoor heat converter 42 of when refrigeration indoor heat converter 42 working as the evaporimeter of cold-producing medium, in addition, also become the refrigerant outlet of when heating indoor heat converter 42 indoor heat converter 42 working as the condenser of cold-producing medium.On current divider 52, be connected with distolateral many (only illustrating the six roots of sensation in Figure 25) the liquid refrigerant pipes 91 that are connected with the first heat-transfer pipe 71 of indoor heat converter 42 of length direction one at indoor heat converter 42.At this, liquid refrigerant pipe 91 consists of capillary.
On gas side tube connector 61, be connected with header box 62, this header box 52 becomes the refrigerant outlet at the indoor heat converter 42 of when refrigeration indoor heat converter 42 working as the evaporimeter of cold-producing medium, in addition, also become the refrigerant inlet of when heating indoor heat converter 42 indoor heat converter 42 working as the condenser of cold-producing medium.On header box 62, be connected with distolateral many (only illustrating the six roots of sensation in Figure 25) the secondary series side gas refrigerant pipes 92 that are connected with the second heat-transfer pipe 72 of indoor heat converter 42 of length direction one at indoor heat converter 42 and distolateral many of being connected with the tertial heat-transfer pipe 72 of indoor heat converter 42 of length direction one (only illustrating the six roots of sensation in Figure 25) the 3rd row side gas refrigerant pipe 93 at indoor heat converter 42.
Indoor heat converter 42 has the refrigerant passage that multistage (only illustrating six sections in Figure 25) forms by connecting the heat-transfer pipe 71,72,73 of one section of three row.Each refrigerant passage has the first heat-transfer pipe 71 being connected with liquid refrigerant pipe 91.The first heat-transfer pipe 71 branching portion 71d between the length direction of indoor heat converter 42 another distolateral and row is connected.Between row, branching portion 71d will flow through the part that the cold-producing medium after the first heat-transfer pipe 71 is divided into two when freezing.Between row, one side of the branch of branching portion 71d is connected at the second heat-transfer pipe 72 of another distolateral upside with being disposed at the first heat-transfer pipe 71 of length direction of indoor heat converter 42.Between row, the opposite side of the branch of branching portion 71d is connected at the 3rd heat-transfer pipe 73 of another distolateral downside with being disposed at the second heat-transfer pipe 72 of length direction of indoor heat converter 42.As shown in figure 26, between row, branching portion 71d is at the pars intermedia of the U-shaped tube portion that the second heat-transfer pipe 72 and the 3rd heat-transfer pipe 73 are linked together to be connected with from the tube portion of the shape of the end of the extended U-shaped tube portion of the first heat-transfer pipe 71.At this, since the extended U-shaped tube portion of the first heat-transfer pipe 71, be set to since the flow path length of the second heat-transfer pipe 72 with identical from the flow path length of the 3rd heat-transfer pipe 73 with the link position between the U-shaped tube portion that the second heat-transfer pipe 72 and the 3rd heat-transfer pipe 73 are linked together.The second heat-transfer pipe 72 is connected with secondary series side gas refrigerant pipe 92 the length direction one of indoor heat converter 42 is distolateral.The 3rd heat-transfer pipe 73b is connected with the 3rd row side gas refrigerant pipe 93 the length direction one of indoor heat converter 42 is distolateral.
By this, in the indoor heat converter 42 of present embodiment, working as the evaporimeter of cold-producing medium in the case of in when refrigeration, the hydraulic fluid side tube connector 51 of the refrigerant inlet when as refrigeration and current divider 52 and flow through a heat-transfer pipe the first heat-transfer pipe 71 in the heat-transfer pipe 71 that cold-producing medium after liquid refrigerant pipe 91 is transported to first row.The cold-producing medium that is transported to the first heat-transfer pipe 71 is flowing through after the first heat-transfer pipe 71, in the outlet of the first heat-transfer pipe 71, is listed as a branching portion 71d and is branched off into i.e. i.e. the 3rd heat-transfer pipe 73 of a heat-transfer pipe in the second heat-transfer pipe 72 and tertial heat-transfer pipe 73 of a heat-transfer pipe in the heat-transfer pipe 72 of secondary series.In addition, the cold-producing medium that is transported to the second heat-transfer pipe 72 is flowing through after the second heat-transfer pipe 72, from the outlet of the second heat-transfer pipe 72, is transported to secondary series side gas refrigerant pipe 92.In addition, the cold-producing medium that is transported to the 3rd heat-transfer pipe 73 is flowing through after the 3rd heat-transfer pipe 73, from the outlet of the 3rd heat-transfer pipe 73, is transported to the 3rd row side gas refrigerant pipe 93.Header box 62 and the gas side tube connector 61 of the refrigerant outlet when flowing through cold-producing medium after secondary series side gas refrigerant pipe 92 and the 3rd row side gas refrigerant pipe 93 and being transported to as refrigeration.
In addition, in the indoor heat converter 42 of present embodiment, working as the condenser of cold-producing medium when heating, via the gas side tube connector 61 of the refrigerant inlet when heating and header box 62 and flow through a heat-transfer pipe the second heat-transfer pipe 72 in the second heat-transfer pipe 72 that cold-producing medium after secondary series side gas refrigerant pipe 92 and the 3rd row side gas refrigerant pipe 93 is transported to secondary series and a heat-transfer pipe the 3rd heat-transfer pipe 73 in tertial the 3rd heat-transfer pipe 73.The cold-producing medium that is transported to the second heat-transfer pipe 72 flows through the second heat-transfer pipe 72.The cold-producing medium that is transported to the 3rd heat-transfer pipe 73 flows through the 3rd heat-transfer pipe 73.Flow through the cold-producing medium of the second heat-transfer pipe 72 and flow through between the cold-producing medium utilization row of the 3rd heat-transfer pipe 73 branching portion 71d at the outlet of the second heat-transfer pipe 72 and the outlet of the 3rd heat-transfer pipe 73 interflow, and be transported to i.e. the first heat-transfer pipe 71 of a heat-transfer pipe in the first heat-transfer pipe 71 of first row.In addition, be transported to the cold-producing medium of the first heat-transfer pipe 71 flowing through after the first heat-transfer pipe 71, be transported to liquid refrigerant pipe 91.Flow through current divider 52 and hydraulic fluid side tube connector 51 that cold-producing medium after liquid refrigerant pipe 91 is transported to the refrigerant outlet when heating.
(2) there is the feature of the indoor unit of indoor heat converter
As having in the indoor unit 4 of ceiling built-in air-conditioning system of indoor heat converter 42 of present embodiment, there is following feature.
(A)
The indoor heat converter 42 of present embodiment has following structure: the refrigerant inlet at the indoor heat converter 42 of when refrigeration indoor heat converter 42 working as the evaporimeter of cold-producing medium is connected with many liquid refrigerant pipes 91, and these many liquid refrigerant pipes 91 are connected with the heat-transfer pipe 71 that the row of weather side in the flow direction of air are first row.In addition, this indoor heat converter 42 has following structure: when refrigeration, the refrigerant outlet of indoor heat converter 42 is connected with many gas refrigerant pipes 92,93, and the part in these many gas refrigerant pipes 92,93 is that secondary series side gas refrigerant pipe 92 is connected with the heat-transfer pipe 72 of secondary series in the flow direction of air.In addition, this indoor heat converter 42 has following structure: the remainder in many gas refrigerant pipes 92,93 i.e. the 3rd row side gas refrigerant pipe 93 is that tertial heat-transfer pipe 73 is connected with the row of downwind side in the flow direction of air.
Therefore, in the indoor unit 4 of present embodiment, during refrigeration, a part for the cold-producing medium that refrigerant inlet during from the refrigeration of indoor heat converter 42 flows into, just having carried out heat exchange with the air of the temperature heat-transfer pipe that passes across secondary series 72 higher than the temperature of air that passes across tertial heat-transfer pipe 73, is just transported to secondary series side gas refrigerant pipe 92.In addition, in this indoor unit 4, during refrigeration, the remainder of the cold-producing medium that the refrigerant inlet during from the refrigeration of indoor heat converter 42 flows into, just having carried out heat exchange with the air that passes across tertial heat-transfer pipe 73, is just transported to the 3rd row side gas refrigerant pipe 93.In addition, flow through cold-producing medium after secondary series side gas refrigerant pipe 92 and the cold-producing medium interflow of flowing through after the 3rd row side gas refrigerant pipe 93, and the refrigerant outlet during from the refrigeration of indoor heat converter 42 flows out.At this, because the degree of superheat of just having carried out the cold-producing medium after heat exchange with the air of heat-transfer pipe 72 that passes across secondary series is subject to the temperature impact of the air of the heat-transfer pipe 72 that passes across secondary series, therefore easily than just and the air that passes across tertial heat-transfer pipe 73 to have carried out the degree of superheat of the cold-producing medium after heat exchange large.
By this, in this indoor unit 4, the degree of superheat of the cold-producing medium that the refrigerant outlet during from the refrigeration of indoor heat converter 42 flows out is all compared easy increase with the structure that tertial heat-transfer pipe 73 is connected by all gas refrigerant pipes 92,93 with adopting, thereby can improve the heat exchanger effectiveness while freezing.
In addition, in this indoor unit 4, while heating, the cold-producing medium that the refrigerant inlet during from the heating of indoor heat converter 42 flows into be all just and the air of the minimum heat-transfer pipe that passes across first row 71 of temperature be just transported to liquid refrigerant pipe 91 having carried out heat exchange.
By this, in this indoor unit 4, the degree of supercooling of refrigerant outlet during the heating of indoor heat converter 42 is difficult for diminishing, thus the reduction of the heat exchanger effectiveness in the time of heating.
As mentioned above, in this indoor unit 4, the degree of supercooling of the refrigerant outlet while making the heating of indoor heat converter 42 is difficult for reducing, and the degree of superheat of the cold-producing medium that flows out of the refrigerant outlet while making the refrigeration from indoor heat converter 42 easily increases, thereby the reduction of the heat exchanger effectiveness of the indoor heat converter 42 in the time of heating, and can improve the heat exchanger effectiveness of the indoor heat converter 42 in when refrigeration.
(B)
In the indoor heat converter 42 of present embodiment, liquid refrigerant pipe 91, secondary series side gas refrigerant pipe 92 and the 3rd row side gas refrigerant pipe 93 connect with length direction one end of corresponding heat- transfer pipe 71,72,73.
By this, in the indoor unit 4 of present embodiment, can be integrated into that the length direction one of indoor heat converter 42 is distolateral carries out the connection operation towards heat- transfer pipe 71,72,73 of liquid refrigerant pipe 91, secondary series side gas refrigerant pipe 92 and the 3rd row side gas refrigerant pipe 93, therefore, can improve the assembleability of indoor heat converter 42.
(C)
The indoor heat converter 42 of present embodiment has in when refrigeration the cold-producing medium of outlet of the heat-transfer pipe 71 that is transported to first row is branched off into branching portion 71d between the heat-transfer pipe 72 of secondary series and the row of tertial heat-transfer pipe 73.In addition in the outlet of the heat-transfer pipe 72 of the secondary series of when refrigeration indoor heat converter 42 working as the evaporimeter of cold-producing medium, be connected with secondary series side gas refrigerant pipe 92.In addition, in the outlet of the tertial heat-transfer pipe 73 of when refrigeration indoor heat converter 42 working as the evaporimeter of cold-producing medium, be connected with the 3rd row side gas refrigerant pipe 93.
In this indoor heat converter 42, during refrigeration, by in the heat-transfer pipe of first row 71 because carrying out heat exchange and be transported in the cold-producing medium branch of rich gas state heat-transfer pipe 72 and the tertial heat-transfer pipe 73 of secondary series with air, therefore, the flow velocity that can suppress the cold-producing medium in rich gas state increases.In addition, in this indoor heat converter 42, while heating, make in the heat-transfer pipe 72 of secondary series because of with air carry out in the cold-producing medium of heat exchange in rich solution state and tertial heat-transfer pipe 73 because carrying out the cold-producing medium interflow of heat exchange in rich solution state with air, and be delivered to the heat-transfer pipe 71 of first row, therefore, can make the flow velocity of the cold-producing medium in rich solution state increase the pyroconductivity of the heat-transfer pipe 71 of first row.
By this, in the indoor unit 4 of present embodiment, between being listed as by utilization, branching portion 71d makes cold-producing medium flow branching suppress the increase of the pressure loss, therefore, can further improve the heat exchanger effectiveness of the indoor heat converter 42 while freezing.Especially, in this indoor unit 4, the flow velocity that can suppress the cold-producing medium in heat-transfer pipe 72 and the tertial heat-transfer pipe 73 of the secondary series that the cold-producing medium of the rich gas state larger on the impact of the pressure loss flows through increases, the heat exchanger effectiveness of the indoor heat converter 42 in the time of therefore, effectively improving refrigeration.In addition, in this indoor unit 4, make the flow velocity of the cold-producing medium in the heat-transfer pipe 71 of the first row that the cold-producing medium of the rich solution state less on the impact of the pressure loss flows through increase pyroconductivity, therefore, it is large that the degree of supercooling of refrigerant outlet during the heating of indoor heat converter 42 easily becomes, thus the reduction of the heat exchanger effectiveness in the time of further suppressing to heat.
(D)
In the indoor heat converter 42 of present embodiment, cold-producing medium flows to the other end in the length direction one end from indoor heat converter 42, the length direction other end of indoor heat converter 42 with branching portion 71d between row in branch or interflow turn back to the mode of one end and flow from the length direction other end of indoor heat converter 42.Therefore for the path of flow of refrigerant, be, the shorter path of round trip on the length direction of indoor heat converter 42 only.
By this, in the indoor unit 4 of present embodiment, can suppress the increase of the pressure loss, therefore, the heat exchanger effectiveness of the indoor heat converter 42 while can further improve refrigeration, in addition, the reduction of the heat exchanger effectiveness of the indoor heat converter 42 in the time of can also further suppressing to heat.
(3) variation 1
Forming in the indoor heat converter 42 (with reference to Figure 25) of above-mentioned indoor unit 4, between row, branching portion 71d links together at the length direction of indoor heat converter 42 another distolateral and second heat-transfer pipe 72 and the 3rd heat-transfer pipe 73 that is disposed at the downside of the second heat-transfer pipe 72.
On the other hand, in the indoor heat converter 42 of indoor unit 4 that forms this variation, as shown in Figure 27 and Figure 28, the second heat-transfer pipe 72 that connects branching portion 71d between row is disposed to the downside that connects the 3rd heat-transfer pipe 73 of branching portion 71d between row.
Therefore,, in this indoor heat converter 42, when refrigeration, because making cold-producing medium, the effect of gravity more easily flows in large quantities the second heat-transfer pipe 72 compared with the 3rd heat-transfer pipe 73.
By this, in the indoor unit 4 of this variation, it is large that the degree of superheat of the cold-producing medium that the refrigerant outlet during from the refrigeration of indoor heat converter 42 flows out easily becomes, thus the heat exchanger effectiveness of the indoor heat converter 42 in the time of further improving refrigeration.
(4) variation 2
Forming in the indoor heat converter 42 (with reference to Figure 25) of above-mentioned indoor unit 4, between row, branching portion 71d is formed as: when refrigeration, the flow path length from the flow path length entrance that export to second heat-transfer pipe 72 of first heat-transfer pipe 72 till and the entrance that export to three heat-transfer pipe 73 from first heat-transfer pipe 72 till of indoor heat converter 42 working as the evaporimeter of cold-producing medium is identical.
On the other hand, in the indoor heat converter 42 of indoor unit 4 that forms this variation, as shown in Figure 29 and Figure 30, using between row, branching portion 71d is formed as: indoor heat converter 42 flow path length till the entrance that exports to the second heat-transfer pipe 72 of the first heat-transfer pipe 71 as the evaporimeter of cold-producing medium works when refrigeration of the flow path length ratio till the entrance that exports to the 3rd heat-transfer pipe 73 of the first heat-transfer pipe 71 is long.More specifically, in this variation, as shown in figure 30, branching portion 71d between row is formed as being at the pars intermedia of the U-shaped tube portion that the first heat-transfer pipe 71 and the second heat-transfer pipe 72 are linked together and is connected with from the tube portion of the shape of the end of the extended U-shaped tube portion of the 3rd heat-transfer pipe 73.
Therefore,, in this indoor heat converter 42, during refrigeration, easily there is more flow of refrigerant till arrive via branching portion 71d between row from the outlet of the first heat-transfer pipe 71 the second heat-transfer pipe 72 that the flow path resistance of entrance is less.
By this, in the indoor unit 4 of this variation, it is large that the degree of superheat of the cold-producing medium that the refrigerant outlet during from the refrigeration of indoor heat converter 42 flows out easily becomes, thus the heat exchanger effectiveness of the indoor heat converter 42 in the time of further improving refrigeration.
(5) variation 3
Also can be used forming the feature of combined deformation example 1 and the feature of variation 2 in the indoor heat converter 42 (with reference to Figure 25) of above-mentioned indoor unit 4.
That is, in the indoor heat converter 42 of indoor unit 4 that forms this variation, as shown in FIG. 31 and 32, identical with variation 1, the second heat-transfer pipe 72 that connects branching portion 71d between row is disposed to the downside that connects the 3rd heat-transfer pipe 73 of branching portion 71d between row.And, in the indoor heat converter 42 of indoor unit 4 that forms this variation, identical with variation 2, using between row, branching portion 71d is formed as: indoor heat converter 42 flow path length till the entrance that exports to the second heat-transfer pipe 72 of the first heat-transfer pipe 71 as the evaporimeter of cold-producing medium works when refrigeration of the flow path length ratio till the entrance that exports to the 3rd heat-transfer pipe 73 of the first heat-transfer pipe 71 is long.
By this, in the indoor unit 4 of this variation, can obtain these two effects of the action effect of variation 1 and the action effect of variation 2.
The indoor heat converter > of < the 3rd embodiment
(1) structure of indoor heat converter
The indoor heat converter 42 of present embodiment adopts following structure: identical with the indoor heat converter 42 of the first embodiment and variation and the second embodiment and variation thereof, as shown in Figures 3 and 4, to at multiple heat- transfer pipes 71,72,73 of internal flow, on above-below direction, be configured to multistage (multirow) for cold-producing medium, and in order to realize high performance, they are arranged to three row in the flow direction from the air that blows out as the indoor fan 41 of centrifugal blower.
As shown in figure 33, the indoor heat converter 42 of present embodiment is different in the structure of liquid refrigerant pipe 91, gas refrigerant pipe 92,93 and refrigerant passage from the indoor heat converter 42 of the first embodiment and variation and the second embodiment and variation thereof, but other structure is identical with the indoor heat converter 42 of the first embodiment and variation and the second embodiment and variation thereof, therefore, description thereof is omitted herein.
On hydraulic fluid side tube connector 51, be connected with current divider 52, this current divider 52 becomes the refrigerant inlet at the indoor heat converter 42 of when refrigeration indoor heat converter 42 working as the evaporimeter of cold-producing medium, in addition, also become the refrigerant outlet of when heating indoor heat converter 42 indoor heat converter 42 working as the condenser of cold-producing medium.The heat-transfer pipe being connected with on current divider 52 in distolateral the first heat-transfer pipe 71 with indoor heat converter 42 of length direction one at indoor heat converter 42 is that the liquid refrigerant pipe 91 that secondary series side heat-transfer pipe 71a is connected is secondary series side liquid refrigerant pipe 91a (only illustrating three in Figure 33).In addition, on current divider 52, be connected with distolateral different the first i.e. the 3rd row side liquid refrigerant pipe 91b (only illustrating three in Figure 33) of the heat-transfer pipe 71 liquid refrigerant pipe that the 3rd row side heat-transfer pipe 71b connects 91 with secondary series side heat-transfer pipe 71a from indoor heat converter 42 of length direction one at indoor heat converter 42.At this, secondary series side liquid refrigerant pipe 91a and the 3rd row side liquid refrigerant pipe 91b consist of capillary.
On gas side tube connector 61, be connected with header box 62, this header box 52 becomes the refrigerant outlet at the indoor heat converter 42 of when refrigeration indoor heat converter 42 working as the evaporimeter of cold-producing medium, in addition, also become the refrigerant inlet of when heating indoor heat converter 42 indoor heat converter 42 working as the condenser of cold-producing medium.On header box 62, be connected with distolateral many (only illustrating the six roots of sensation in Figure 33) the secondary series side gas refrigerant pipes 92 that are connected with the second heat-transfer pipe 72 of indoor heat converter 42 of length direction one at indoor heat converter 42 and distolateral many of being connected with the tertial heat-transfer pipe 72 of indoor heat converter 42 of length direction one (only illustrating the six roots of sensation in Figure 33) the 3rd row side gas refrigerant pipe 93 at indoor heat converter 42.
Indoor heat converter 42 has: the first refrigerant passage forming by connecting the heat-transfer pipe 71,72 of two sections of two row; And the second refrigerant path forming by connecting the heat-transfer pipe 71,73 of two sections of two row.The first refrigerant passage and second refrigerant path dispose multistage (in Figure 33, each refrigerant passage only illustrates three sections) alternately.The first refrigerant passage has the secondary series side heat-transfer pipe 71a being connected with secondary series side liquid refrigerant pipe 91a in the first heat-transfer pipe 71.At the length direction of indoor heat converter 42, another is distolaterally connected with branching portion 71g in secondary series secondary series side heat-transfer pipe 71a.In secondary series, branching portion 71g will flow through the part that the cold-producing medium after secondary series side heat-transfer pipe 71a is divided into two when freezing.At the length direction of indoor heat converter 42, another is distolaterally connected with the second heat-transfer pipe 72 being disposed at than the upside place of high one section of secondary series side heat-transfer pipe 71a a side of the branch of branching portion 71g in secondary series.At the length direction of indoor heat converter 42, another is distolaterally connected with the second heat-transfer pipe 72 being disposed at than the downside place of low one section of secondary series side heat-transfer pipe 71a the opposite side of the branch of branching portion 71g in secondary series.As shown in figure 34, branching portion 71d is at the pars intermedia of the U-shaped tube portion that two 72 of the second heat-transfer pipes are linked together to be connected with from the tube portion of the shape of the end of the extended U-shaped tube portion of secondary series side heat-transfer pipe 71a in secondary series.Two the second heat-transfer pipes 72 are connected with secondary series side gas refrigerant pipe 92 respectively the length direction one of indoor heat converter 42 is distolateral.Second refrigerant path has the 3rd row side heat-transfer pipe 71b being connected with the 3rd row side liquid refrigerant pipe 91b in the first heat-transfer pipe 71.At the length direction of indoor heat converter 42, another is distolaterally connected with branching portion 71h in the 3rd row the 3rd row side heat-transfer pipe 71b.In the 3rd row, branching portion 71h will flow through the part that the cold-producing medium after the 3rd row side heat-transfer pipe 71b is divided into two when freezing.In the 3rd row, at the length direction of indoor heat converter 42, another is distolaterally connected with the 3rd heat-transfer pipe 73 being disposed at than the upside place of high two sections of the 3rd row side heat-transfer pipe 71b a side of the branch of branching portion 71h.In the 3rd row the opposite side of the branch of branching portion 71h the length direction of indoor heat converter 42 another distolateral be disposed at the 3rd heat-transfer pipe 73 that the section identical with the 3rd row side heat-transfer pipe 71b locate and connect.As shown in figure 34, in the 3rd row, branching portion 71h is at the pars intermedia of the U-shaped tube portion that two 73 of the 3rd heat-transfer pipes are linked together to be connected with from the tube portion of the shape of the end of the extended U-shaped tube portion of the 3rd row side heat-transfer pipe 71b.Two the 3rd heat-transfer pipes 73 are connected with the 3rd row side gas refrigerant pipe 93 respectively the length direction one of indoor heat converter 42 is distolateral.
By this, in the indoor heat converter 42 of present embodiment, working as the evaporimeter of cold-producing medium in the case of in when refrigeration, the hydraulic fluid side tube connector 51 of the refrigerant inlet when as refrigeration and current divider 52 and flow through a heat-transfer pipe secondary series side heat-transfer pipe 71a in the heat-transfer pipe 71 that many cold-producing mediums after part secondary series side liquid refrigerant pipe 91a in liquid refrigerant pipe 91 are transported to first row.The cold-producing medium that is transported to secondary series side heat-transfer pipe 71a is flowing through after secondary series side heat-transfer pipe 71a, the outlet of secondary series side heat-transfer pipe 71a by secondary series in branching portion 71g be branched off into the second heat-transfer pipe 72 of two secondary series.In addition, be transported to the cold-producing medium of two the second heat-transfer pipes 72 flowing through after each the second heat-transfer pipe 72, from the outlet of each the second heat-transfer pipe 72, be transported to secondary series side gas refrigerant pipe 92.In addition, via hydraulic fluid side tube connector 51 and the current divider 52 of the refrigerant inlet as when refrigeration and flow through cold-producing medium after many remainders in liquid refrigerant pipe 91 the 3rd row side liquid refrigerant pipe 91b and be transported to heat-transfer pipe 71 the 3rd row side heat-transfer pipe 71b of the first row different from secondary series side heat-transfer pipe 71a.The cold-producing medium that is transported to the 3rd row side heat-transfer pipe 71b is flowing through after the 3rd row side heat-transfer pipe 71b, and in the outlet of the 3rd row side heat-transfer pipe 71b is listed as by the 3rd, branching portion 71h is branched off into two tertial the 3rd heat-transfer pipes 73.In addition, the cold-producing medium that is transported to two the 3rd heat-transfer pipes 73 is flowing through after each the 3rd heat-transfer pipe 73, from the outlet of each the 3rd heat-transfer pipe 73, is transported to the 3rd row side gas refrigerant pipe 93.Header box 62 and the gas side tube connector 61 of the refrigerant outlet when flowing through cold-producing medium after secondary series side gas refrigerant pipe 92 and the 3rd row side gas refrigerant pipe 93 and being transported to as refrigeration.
In addition, in the indoor heat converter 42 of present embodiment, working as the condenser of cold-producing medium, via gas side tube connector 61 and the header box 62 of the refrigerant inlet when heating the cold-producing medium that flows through secondary series side gas refrigerant pipe 92, be transported to the second heat-transfer pipe 72 of two secondary series when heating.Flow through two cold-producing mediums after the second heat-transfer pipe 72 and utilize in secondary series branching portion 71g at the outlet interflow of two the second heat-transfer pipes 72, and the heat-transfer pipe being transported in the first heat-transfer pipe 71 of first row is secondary series side heat-transfer pipe 71a.In addition, the cold-producing medium that is transported to secondary series side heat-transfer pipe 71a is flowing through after secondary series side heat-transfer pipe 71a, is transported to secondary series side liquid refrigerant pipe 91a.In addition, via gas side tube connector 61 and the header box 62 of the refrigerant inlet when heating the cold-producing medium flowing through after the 3rd row side gas refrigerant pipe 93, be transported to two tertial the 3rd heat-transfer pipes 73.Flow through two cold-producing mediums after the 3rd heat-transfer pipe 73 and utilize branching portion 71h in the 3rd row to collaborate in the outlet of two the 3rd heat-transfer pipes 72, and be transported to i.e. the 3rd row side heat-transfer pipe 71b of heat-transfer pipe 71 of the first row different from secondary series side heat-transfer pipe 71a.In addition, the cold-producing medium that is transported to the 3rd row side heat-transfer pipe 71b is flowing through after the 3rd row side heat-transfer pipe 71b, is transported to the 3rd row side liquid refrigerant pipe 91b.In addition, flow through the cold-producing medium after secondary series side liquid refrigerant pipe 91a and flow through cold-producing medium after the 3rd row side liquid refrigerant pipe 91b the current divider 52 and the hydraulic fluid side tube connector 51 that are transported to the refrigerant outlet when heating.
(2) there is the feature of the indoor unit of indoor heat converter
As having in the indoor unit 4 of ceiling built-in air-conditioning system of indoor heat converter 42 of present embodiment, there is following feature.
(A)
The indoor heat converter 42 of present embodiment has following structure: the refrigerant inlet at the indoor heat converter 42 of when refrigeration indoor heat converter 42 working as the evaporimeter of cold-producing medium is connected with many liquid refrigerant pipes 91, and these many liquid refrigerant pipes 91 are connected with the heat-transfer pipe 71 that the row of weather side in the flow direction of air are first row.In addition, this indoor heat converter 42 has following structure: when refrigeration, the refrigerant outlet of indoor heat converter 42 is connected with many gas refrigerant pipes 92,93, and the part in these many gas refrigerant pipes 92,93 is that secondary series side gas refrigerant pipe 92 is connected with the heat-transfer pipe 72 of secondary series in the flow direction of air.In addition, this indoor heat converter 42 has following structure: the remainder in many gas refrigerant pipes 92,93 i.e. the 3rd row side gas refrigerant pipe 93 is that tertial heat-transfer pipe 73 is connected with the row of downwind side in the flow direction of air.
Therefore, in the indoor unit 4 of present embodiment, during refrigeration, a part for the cold-producing medium that refrigerant inlet during from the refrigeration of indoor heat converter 42 flows into, just having carried out heat exchange with the air of the temperature heat-transfer pipe that passes across secondary series 72 higher than the temperature of air that passes across tertial heat-transfer pipe 73, is just transported to secondary series side gas refrigerant pipe 92.In addition, in this indoor unit 4, during refrigeration, the remainder of the cold-producing medium that the refrigerant inlet during from the refrigeration of indoor heat converter 42 flows into, just having carried out heat exchange with the air that passes across tertial heat-transfer pipe 73, is just transported to the 3rd row side gas refrigerant pipe 93.In addition, flow through cold-producing medium after secondary series side gas refrigerant pipe 92 and the cold-producing medium interflow of flowing through after the 3rd row side gas refrigerant pipe 93, and the refrigerant outlet during from the refrigeration of indoor heat converter 42 flows out.At this, because the degree of superheat of just having carried out the cold-producing medium after heat exchange with the air of heat-transfer pipe 72 that passes across secondary series is subject to the temperature impact of the air of the heat-transfer pipe 72 that passes across secondary series, therefore easily than just and the air that passes across tertial heat-transfer pipe 73 to have carried out the degree of superheat of the cold-producing medium after heat exchange large.
By this, in this indoor unit 4, the degree of superheat of the cold-producing medium that the refrigerant outlet during from the refrigeration of indoor heat converter 42 flows out is all compared easy increase with the structure that tertial heat-transfer pipe 73 is connected by all gas refrigerant pipes 92,93 with adopting, thereby can improve the heat exchanger effectiveness while freezing.
In addition, in this indoor unit 4, while heating, the cold-producing medium that the refrigerant inlet during from the heating of indoor heat converter 42 flows into be all just and the air of the minimum heat-transfer pipe that passes across first row 71 of temperature be just transported to liquid refrigerant pipe 91 having carried out heat exchange.
By this, in this indoor unit 4, the degree of supercooling of refrigerant outlet during the heating of indoor heat converter 42 is difficult for diminishing, thus the reduction of the heat exchanger effectiveness in the time of heating.
As mentioned above, in this indoor unit 4, the degree of supercooling of the refrigerant outlet while making the heating of indoor heat converter 42 is difficult for reducing, and the degree of superheat of the cold-producing medium that flows out of the refrigerant outlet while making the refrigeration from indoor heat converter 42 easily increases, thereby the reduction of the heat exchanger effectiveness of the indoor heat converter 42 in the time of heating, and can improve the heat exchanger effectiveness of the indoor heat converter 42 in when refrigeration.
(B)
In the indoor heat converter 42 of present embodiment, liquid refrigerant pipe 91, secondary series side gas refrigerant pipe 92 and the 3rd row side gas refrigerant pipe 93 connect with length direction one end of corresponding heat- transfer pipe 71,72,73.
By this, in the indoor unit 4 of present embodiment, can be integrated into that the length direction one of indoor heat converter 42 is distolateral carries out the connection operation towards heat- transfer pipe 71,72,73 of liquid refrigerant pipe 91, secondary series side gas refrigerant pipe 92 and the 3rd row side gas refrigerant pipe 93, therefore, can improve the assembleability of indoor heat converter 42.
(C)
In the indoor heat converter 42 of present embodiment, during refrigeration, a part for cold-producing medium is delivered to secondary series side refrigerant pipe 71a via secondary series side liquid refrigerant pipe 91a, by in secondary series side heat-transfer pipe 71a because carrying out heat exchange and be transported in the cold-producing medium branch of rich gas state the heat-transfer pipe 72 of two secondary series with air, and the remainder of cold-producing medium is delivered to the 3rd row side refrigerant pipe 71b via the 3rd row side liquid refrigerant pipe 91b, to in the 3rd row side heat-transfer pipe 71b, because carrying out heat exchange with air, in the cold-producing medium branch of rich gas state, be transported to two tertial heat-transfer pipes 73, therefore, the flow velocity that can suppress the cold-producing medium in rich gas state increases.
In addition, in the indoor heat converter 42 of present embodiment, while heating, make in the heat-transfer pipe 72 of two secondary series because of with air carry out in the cold-producing medium of heat exchange in rich solution state and two tertial heat-transfer pipes 73 because carrying out the cold-producing medium interflow of heat exchange in rich solution state with air, and be delivered to secondary series side heat-transfer pipe 71a, the 3rd row side heat-transfer pipe 71b, therefore, can make the flow velocity of the cold-producing medium in rich solution state increase the pyroconductivity of secondary series side heat-transfer pipe 71a, the 3rd row side heat-transfer pipe 71b.
In addition, in the indoor heat converter 42 of present embodiment, during refrigeration, making, in the stage of the liquid refrigerant pipe 91 of cold-producing medium before flowing through the heat-transfer pipe 71 of first row, cold-producing medium to be branched off into secondary series side liquid refrigerant pipe 91a and the 3rd row side liquid refrigerant pipe 91b.
And, in the indoor heat converter 42 of present embodiment, cold-producing medium flows to the other end in the length direction one end from indoor heat converter 42, the length direction other end of indoor heat converter 42 with branching portion 71g, 71h in row in branch or interflow from the length direction other end of indoor heat converter 42, turn back mobile to the mode of one end.Therefore for the path of flow of refrigerant, be, the shorter path of round trip on the length direction of indoor heat converter 42 only.
By this, in the indoor unit 4 of present embodiment, can, by utilizing branching portion 71h in branching portion 71g in secondary series, the 3rd row to make cold-producing medium flow branching suppress the increase of the pressure loss, therefore, can further improve the heat exchanger effectiveness of the indoor heat converter 42 while freezing.Especially, in this indoor unit 4, the flow velocity that can suppress the cold-producing medium in heat-transfer pipe 72 and the tertial heat-transfer pipe 73 of the secondary series that the cold-producing medium of the rich gas state larger on the impact of the pressure loss flows through increases, the heat exchanger effectiveness of the indoor heat converter 42 in the time of therefore, effectively improving refrigeration.In addition, in this indoor unit 4, make the flow velocity of the cold-producing medium in secondary series side heat-transfer pipe 71a, the 3rd row side heat-transfer pipe 71b that the cold-producing medium of the rich solution state less on the impact of the pressure loss flows through increase pyroconductivity, therefore, it is large that the degree of supercooling of refrigerant outlet during the heating of indoor heat converter 42 easily becomes, thus the reduction of the heat exchanger effectiveness in the time of further suppressing to heat.
(3) variation 1
In the indoor heat converter 42 of indoor unit 4 that forms this variation, in the indoor heat converter 42 (with reference to Figure 33) of the above-mentioned indoor unit 4 of formation, the bore that makes the 3rd row side liquid refrigerant pipe 71b is less than the bore of one section of upside place at the 3rd row side liquid refrigerant pipe 71b or the adjacent secondary series side liquid refrigerant pipe 71a in one section of downside place, or the length of tube that makes the 3rd row side liquid refrigerant pipe 71b is longer than the length of tube of one section of upside place at the 3rd row side liquid refrigerant pipe 71b or the adjacent secondary series side liquid refrigerant pipe 71a in one section of downside place.
Therefore, in the indoor heat converter 42 of this variation, during refrigeration, easily there is more flow of refrigerant in the less secondary series side liquid refrigerant pipe 71a of flow path resistance, therefore, compared with tertial heat-transfer pipe 73, have more flow of refrigerant in the heat-transfer pipe 72 of secondary series.
By this, in the indoor unit 4 of this variation, it is large that the degree of superheat of the cold-producing medium that the refrigerant outlet during from the refrigeration of indoor heat converter 42 flows out easily becomes, thus the heat exchanger effectiveness of the indoor heat converter 42 in the time of further improving refrigeration.
Other embodiment of < >
Above, with reference to the accompanying drawings embodiments of the present invention and variation thereof are illustrated, but concrete structure is not limited to these embodiments and variation thereof, can in the scope of main points that does not depart from invention, changes.
(A)
For example, in above-mentioned embodiment and variation thereof, to using example of the present invention to be illustrated in the ceiling built-in air-conditioning system of ceiling type, but be not limited to this, also can in the ceiling built-in air-conditioning system that installs the pattern that be called as ceiling mounting type of configured in one piece below ceiling, use the present invention.
Particularly, can in the indoor unit 104 shown in Figure 35 and Figure 36, use the present invention.
Indoor unit 104 has the housing 131 of receiving various constitution equipments in inside.Under the state that housing 131 is configured to contact with the ceiling of air conditioning chamber at its end face, hanging is in air conditioning chamber.Indoor unit 104 is identical with above-mentioned embodiment and variation thereof, via liquid refrigerant communicating pipe (not shown) and gas refrigerant communicating pipe (not shown), be connected with outdoor unit (not shown), thereby form the refrigerant loop (not shown) of steam compression type.
Housing 131 is to overlook to be roughly tetragonal box-shaped body, has: be roughly tetragonal top board 133; The side plate 134 extending towards below from the circumference of top board 133; And be roughly tetragonal base plate 132.Top board 133 forms for the part for indoor heat converter 142 (aftermentioned) and the hydraulic fluid side tube connector 51 linking together cold-producing medium communicating pipe (not shown) and gas side tube connector 61 are run through.Side plate 134 consists of side plate 134a, 134b, 134c, the 134d on the each limit corresponding to top board 133 and base plate 134.On each side plate 134a, 134b, 134c, 134d, be provided with blow- off outlet 136a, 136b, 136c, 136d.On each blow- off outlet 136a, 136b, 136c, 136d, be provided with horizontal tail 139a, the 139b, 139c, the 139d that to blowing out, to the wind direction of the air in air conditioning chamber, regulate.At the substantial middle place of base plate 132, be provided with the suction inlet 135 that sucks the air in air conditioning chamber.Suction inlet 135 is to be roughly tetragonal opening.
At the internal main of housing 131, to dispose indoor fan 141 and indoor heat converter 142, wherein, above-mentioned indoor fan 141 is as centrifugal blower, air in air conditioning chamber, via in suction inlet 135 suction casings 131, and is blown out in housing 131 via blow- off outlet 136a, 136b, 136c, 136d.
The structure of indoor fan 141 is identical with the structure of the indoor fan 41 of above-mentioned embodiment and variation thereof, can from below air amount and towards overlook observe time outer circumferential side blow out.
Indoor heat converter 142 is the fin tube type heat exchangers that are disposed at the outer circumferential side of overlooking the indoor fan 141 while observing.More specifically, indoor heat converter 142 is bent the surrounding being configured to indoor fan 141 and surrounds, be to be called as the finned fin tube type heat exchanger of intersection, there are the multiple heat-transfer pipes that arrange across many thermofins of predetermined distance configuration with to run through the state of these thermofins along thickness of slab direction.The hydraulic fluid side of indoor heat converter 142 is connected with liquid refrigerant communicating pipe (not shown) via hydraulic fluid side tube connector 51, and the gas side of indoor heat converter 141 is connected with gas refrigerant communicating pipe (not shown) via gas side tube connector 61.In addition, indoor heat converter 142 works as the evaporimeter of cold-producing medium when refrigeration, and the condenser as cold-producing medium when heating works.By this, indoor heat converter 142 carries out heat exchange with the air blowing out from indoor fan 141, thus can be when refrigeration cooling-air, when heating, add hot-air.In addition, the structure of indoor heat converter 142 is identical with the structure of the indoor heat converter 42 of above-mentioned embodiment and variation thereof.Therefore, the indoor heat converter of above-mentioned embodiment and variation thereof 42 and heat exchange department 42a, 42b, 42c are replaced with to indoor heat converter 142 and heat exchange department 142a, 142b, 142c, description thereof is omitted herein.In addition, at the downside of indoor heat converter 142, dispose the drain pan 140 of the drain water producing for the moisture of admission of air is condensed in indoor heat converter 142.Drain pan 140 is installed on the bottom of housing 131.
In addition,, in the indoor unit 104 of this ceiling mounting type, also can obtain the action effect identical with the action effect of above-mentioned embodiment and variation thereof.
(B)
In addition, in above-mentioned embodiment and variation thereof, to using example of the present invention to be illustrated to surround mode around the suction inlet of overlooking while observing in being provided with the ceiling built-in air-conditioning system that is called as multi-directional airflow formula of blow-off outlet, but be not limited to this, also can in the ceiling built-in air-conditioning system that is called as two-way airflow formula of overlooking the both sides of suction inlet while observing and be provided with blow-off outlet, use the present invention.
Particularly, can in the indoor unit 204 shown in Figure 37 and Figure 38, use the present invention.
Indoor unit 204 has the housing 231 of receiving various constitution equipments in inside.Housing 231 consists of with the decoration panel 232 that is disposed at housing body 231a downside housing body 231a.Housing body 231a is identical with above-mentioned embodiment and variation thereof, is configured to be inserted in the opening forming on the ceiling of air conditioning chamber.In addition, decoration panel 232 is identical with above-mentioned embodiment and variation thereof, is configured to embed the opening of ceiling.Indoor unit 204 is identical with above-mentioned embodiment and variation thereof, is connected, thereby forms the refrigerant loop of steam compression type via liquid refrigerant communicating pipe 5 and gas refrigerant communicating pipe 6 with outdoor unit.
Housing body 231a overlooks to be the roughly box-shaped body of tetragonal lower surface opening, has: be roughly tetragonal top board 233; And the side plate 234 extending towards below from the circumference of top board 233.Side plate 234 forms by side plate 234a, the 234b on the long limit corresponding to top board 233 with corresponding to side plate 234c, the 234d of the minor face of top board 233.Side plate 234d forms for the part for indoor heat converter 242 (aftermentioned) and the hydraulic fluid side tube connector 51 linking together cold-producing medium communicating pipe 5,6 and gas side tube connector 61 are run through.
Decoration panel 232 is to overlook to be roughly tetragonal plate body, mainly the panel body 232a that is fixed on housing body 231a bottom, consists of.Panel body 232a has: the suction inlet 235 that sucks the air in air conditioning chamber; And blow-off outlet 236a, the 236b towards the blow out air in air conditioning chamber that along the long limits of two of this panel body 232a, form.Suction inlet 235 is sandwiched between blow-off outlet 236a and blow-off outlet 236b.
At the internal main of housing body 231a, to dispose indoor fan 241 and indoor heat converter 242, wherein, above-mentioned indoor fan 241 is as centrifugal blower, in suction inlet 235 suction casing main body 231a by the air in air conditioning chamber via decoration panel 232, and blow out in housing body 231a via blow-off outlet 236a, the 236b of decoration panel 232.
Indoor fan 241 has: the fan motor 241a that is located at the substantial middle place in housing body 231a; And multiple (being two herein) impeller 241b that is connected with fan motor 241a and is driven in rotation.Each impeller 241b is double suction wind multiple wing impeller, and the interior air amount of volute type casing 241c of each impeller 241b is accommodated by its court, and blows out this air from the opening 241d that blows out of volute type casing 241c.
Indoor heat converter 242 is the fin tube type heat exchangers that are disposed at the outer circumferential side of overlooking the indoor fan 241 while observing.More specifically, indoor heat converter 242 has roughly two indoor heat converters 243,244 that long limit configures along top board 233.Indoor heat converter the 243, the 244th, has across being called as of many thermofins of predetermined distance configuration and many heat-transfer pipes arranging under the state that these thermofins are run through along thickness of slab direction and intersects finned fin tube type heat exchanger.The both ends of the first indoor heat converter 243 are towards the second indoor heat converter 244 lateral bends, and the both ends of the second indoor heat converter 244 are towards the first indoor heat converter 243 lateral bends.That is, indoor heat converter 242 entirety are bent and are configured to surround indoor fan 241 around.The hydraulic fluid side of indoor heat converter 242 is through being connected with liquid refrigerant communicating pipe 5 by hydraulic fluid side tube connector 51 after collaborate in current divider 52 hydraulic fluid side of each indoor heat converter 243,244, and the gas side of indoor heat converter 241 warp after the gas side of each indoor heat converter 243,244 collaborates in header box 62 is connected with gas refrigerant communicating pipe 6 by gas side tube connector 61.In addition, indoor heat converter 242 works as the evaporimeter of cold-producing medium when refrigeration, and the condenser as cold-producing medium when heating works.By this, indoor heat converter 242 carries out heat exchange with the air blowing out from indoor fan 141, thus can be when refrigeration cooling-air, when heating, add hot-air.In addition, except by utilizing two indoor heat converters 243,244 that current divider 52 and header box 62 link together to form this point, the structure of indoor heat converter 242 is identical with the indoor heat converter 42 of above-mentioned embodiment and variation thereof.Therefore, the indoor heat converter of above-mentioned embodiment and variation thereof 42 and heat exchange department 42a, 42b, 42c are replaced with to indoor heat converter 242 (being indoor heat converter 243,244) and heat exchange department 242a, 242b, 242c, and description thereof is omitted herein.In addition, at the downside of indoor heat converter 242, dispose the drain pan 240 of the drain water producing for the moisture of admission of air is condensed in indoor heat converter 242.Drain pan 140 is installed on the bottom of housing body 231a.In addition, on drain pan 240, be formed with and blow out hole 240a, 240b and inlet hole (not shown), wherein, above-mentioned hole 240a, the 240b of blowing out is communicated with blow-off outlet 236a, the 236b of decoration panel 232, and above-mentioned inlet hole is communicated with and reception room internal fan 241 with the suction inlet 235 of decoration panel 232.
In addition,, in the indoor unit 204 of this two-way airflow formula, also can obtain the action effect identical with the action effect of above-mentioned embodiment and variation thereof.
Industrial utilizability
The present invention can be widely used in the ceiling built-in air-conditioning system of structure that has the indoor heat converter consisting of fin tube type heat exchanger and be disposed at the outer circumferential side of overlooking the centrifugal blower while observing.
(symbol description)
4,104,204 indoor units (ceiling built-in air-conditioning system)
41,141,241 indoor fans (centrifugal blower)
42,142,242 indoor heat converters
71 first heat-transfer pipes
71a, 71e the first upstream side heat-transfer pipe, secondary series side heat-transfer pipe
71b, 71f the first downstream heat-transfer pipe, the 3rd row side heat-transfer pipe
Branching portion between 71d row
Branching portion in 71g secondary series
Branching portion in 71h the 3rd row
72 second heat-transfer pipes
72a, 72e the second upstream side heat-transfer pipe
72b, 72f the second downstream heat-transfer pipe
73 the 3rd heat-transfer pipes
73a, 73e the 3rd upstream side heat-transfer pipe
73b, 73f the 3rd downstream heat-transfer pipe
91 liquid refrigerant pipes
91a secondary series side liquid refrigerant pipe
91b the 3rd row side liquid refrigerant pipe
92 secondary series side gas refrigerant pipes
93 the 3rd row side gas refrigerant pipes
Prior art document
Patent documentation
Patent documentation 1: Japanese Patent Laid-Open 2009-30827 communique

Claims (18)

1. a ceiling built-in air-conditioning system (4,104,204), there is the structure that the indoor heat converter (42,142,242) consisting of fin tube type heat exchanger is disposed at the outer circumferential side of overlooking the centrifugal blower (41,141,241) while observing, it is characterized in that
Described indoor heat converter has following structure:
The many heat-transfer pipes (71,72,73) that flow therein for cold-producing medium are arranged in multistage on above-below direction, and are arranged with three row in the flow direction of the air blowing out from described centrifugal blower,
The refrigerant inlet of the described indoor heat converter in the case of indoor heat converter described in when refrigeration works as the evaporimeter of cold-producing medium is connected with many liquid refrigerant pipes (91), these many liquid refrigerant pipes (91) are connected with the heat-transfer pipe (71) that the row of weather side in the flow direction of described air are first row
Described in when refrigeration, the refrigerant outlet of indoor heat converter is connected with many gas refrigerant pipes (92,93), a part in these many gas refrigerant pipes (92,93) is that secondary series side gas refrigerant pipe is connected with the heat-transfer pipe (72) of secondary series in the flow direction of described air
Remainder in described many gas refrigerant pipes i.e. the 3rd row side gas refrigerant pipe is that tertial heat-transfer pipe (73) is connected with the row of downwind side in the flow direction of described air,
Described indoor heat converter (42,142,242) has branching portion between row (71d), branching portion between these row (71d) is branched off into the cold-producing medium that is transported to the outlet of the heat-transfer pipe (71) of described first row when freezing heat-transfer pipe (72) and the described tertial heat-transfer pipe (73) of described secondary series
The outlet of the heat-transfer pipe of the described secondary series in the case of indoor heat converter described in when refrigeration works as the evaporimeter of cold-producing medium is connected with described secondary series side gas refrigerant pipe (92),
The outlet of the described tertial heat-transfer pipe in the case of indoor heat converter described in when refrigeration works as the evaporimeter of cold-producing medium is connected with described the 3rd row side gas refrigerant pipe (93).
2. ceiling built-in air-conditioning system as claimed in claim 1 (4,104,204), is characterized in that,
Described liquid refrigerant pipe (91) is connected with length direction one end of the heat-transfer pipe (71) of described first row, described secondary series side gas refrigerant pipe (92) is connected with length direction one end of the heat-transfer pipe (72) of described secondary series, and described the 3rd row side gas refrigerant pipe (93) is connected with length direction one end of described tertial heat-transfer pipe (73).
3. ceiling built-in air-conditioning system as claimed in claim 1 (4,104,204), is characterized in that,
During refrigeration, flow through a heat-transfer pipe the first upstream side heat-transfer pipe (71a in the heat-transfer pipe (71) that cold-producing medium after described liquid refrigerant pipe (91) is transported to described first row, 71e), this cold-producing medium is flowing through after described the first upstream side heat-transfer pipe, also flow through the i.e. first downstream heat-transfer pipe (71b) of heat-transfer pipe of the described first row different from described the first upstream side heat-transfer pipe, and in the outlet of described the first downstream heat-transfer pipe, by branching portion (71d) between described row, be branched off into i.e. the second upstream side heat-transfer pipe (72a of a heat-transfer pipe in the heat-transfer pipe (72) of described secondary series, heat-transfer pipe 72e) and in described tertial heat-transfer pipe (73) i.e. the 3rd upstream side heat-transfer pipe (73a, 73e),
The cold-producing medium that is transported to described the second upstream side heat-transfer pipe is flowing through after described the second upstream side heat-transfer pipe, also flow through the i.e. second downstream heat-transfer pipe (72b, 72f) of heat-transfer pipe of the described secondary series different from described the second upstream side heat-transfer pipe, and be transported to described secondary series side gas refrigerant pipe (92) from the outlet of described the second downstream heat-transfer pipe
The cold-producing medium that is transported to described the 3rd upstream side heat-transfer pipe is flowing through after described the 3rd upstream side heat-transfer pipe, also flow through i.e. the 3rd downstream heat-transfer pipe (73b, 73f) of the described tertial heat-transfer pipe different from described the 3rd upstream side heat-transfer pipe, and be transported to described the 3rd row side gas refrigerant pipe (93) from the outlet of described the 3rd downstream heat-transfer pipe.
4. ceiling built-in air-conditioning system as claimed in claim 3 (4,104,204), is characterized in that,
Described the second upstream side heat-transfer pipe (72a) is disposed at the downside of described the 3rd upstream side heat-transfer pipe (73a).
5. ceiling built-in air-conditioning system as claimed in claim 3 (4,104,204), is characterized in that,
Branching portion between described row (71d) is formed as: the flow path length till the entrance of described the second upstream side heat-transfer pipe (72a) of exporting to of described the first downstream heat-transfer pipe (71b) from indoor heat converter (42,142,242) described in flow path length till the entrance of described the 3rd upstream side heat-transfer pipe (73a) of exporting to of described the first downstream heat-transfer pipe is when in refrigeration works as the evaporimeter of cold-producing medium is long.
6. ceiling built-in air-conditioning system as claimed in claim 4 (4,104,204), is characterized in that,
Branching portion between described row (71d) is formed as: the flow path length till the entrance of described the second upstream side heat-transfer pipe (72a) of exporting to of described the first downstream heat-transfer pipe (71b) from indoor heat converter (42,142,242) described in flow path length till the entrance of described the 3rd upstream side heat-transfer pipe (73a) of exporting to of described the first downstream heat-transfer pipe is when in refrigeration works as the evaporimeter of cold-producing medium is long.
7. the ceiling built-in air-conditioning system as described in any one in claim 3 to 6 (4,104,204), is characterized in that,
Described the 3rd downstream heat-transfer pipe (73b) is disposed at the upside of described the 3rd upstream side heat-transfer pipe (73a).
8. the ceiling built-in air-conditioning system as described in any one in claim 3 to 6 (4,104,204), is characterized in that,
Described the second downstream heat-transfer pipe (72b) is disposed at the upside of described the second upstream side heat-transfer pipe (72a).
9. ceiling built-in air-conditioning system as claimed in claim 7 (4,104,204), is characterized in that,
Described the second downstream heat-transfer pipe (72b) is disposed at the upside of described the second upstream side heat-transfer pipe (72a).
10. the ceiling built-in air-conditioning system as described in any one in claim 3 to 6 (4,104,204), is characterized in that,
Described the first downstream heat-transfer pipe (71b) is disposed at the upside of described the first upstream side heat-transfer pipe (71a).
11. ceiling built-in air-conditioning systems as claimed in claim 7 (4,104,204), is characterized in that,
Described the first downstream heat-transfer pipe (71b) is disposed at the upside of described the first upstream side heat-transfer pipe (71a).
12. ceiling built-in air-conditioning systems as claimed in claim 8 (4,104,204), is characterized in that,
Described the first downstream heat-transfer pipe (71b) is disposed at the upside of described the first upstream side heat-transfer pipe (71a).
13. ceiling built-in air-conditioning systems as claimed in claim 3 (4,104,204), is characterized in that,
The outlet of described the second downstream heat-transfer pipe (72b) in the case of indoor heat converter (42,142,242) described in when refrigeration works as the evaporimeter of cold-producing medium and the outlet of described the 3rd downstream heat-transfer pipe (73b) are configured to be disposed at described in another of upside or downside outlet of the second downstream heat-transfer pipe (72f) and the outlet of described the 3rd downstream heat-transfer pipe (73f) adjacent
The entrance of described the first upstream side heat-transfer pipe (71a) in the case of indoor heat converter described in when refrigeration works as the evaporimeter of cold-producing medium is configured to be disposed at described in another of upside or downside entrance of the first upstream side heat-transfer pipe (71e) adjacent.
14. ceiling built-in air-conditioning systems as claimed in claim 1 (4,104,204), is characterized in that,
During refrigeration, flow through heat-transfer pipe first heat-transfer pipe (71) in the heat-transfer pipe that cold-producing medium after described liquid refrigerant pipe (91) is transported to described first row, and flowing through after described the first heat-transfer pipe, in the outlet of described the first heat-transfer pipe, by branching portion (71d) between described row, be branched off into a heat-transfer pipe in the heat-transfer pipe of described secondary series a heat-transfer pipe in the second heat-transfer pipe (72) and described tertial heat-transfer pipe be the 3rd heat-transfer pipe (73)
Be transported to the cold-producing medium of described the second heat-transfer pipe flowing through after described the second heat-transfer pipe, from the outlet of described the second heat-transfer pipe, be transported to described secondary series side gas refrigerant pipe (92),
The cold-producing medium that is transported to described the 3rd heat-transfer pipe is flowing through after described the 3rd heat-transfer pipe, from the outlet of described the 3rd heat-transfer pipe, is transported to described the 3rd row side gas refrigerant pipe (93).
15. ceiling built-in air-conditioning systems as claimed in claim 14 (4,104,204), is characterized in that,
Described the second heat-transfer pipe (72) is disposed at the downside of described the 3rd heat-transfer pipe (73).
16. ceiling built-in air-conditioning systems (4,104,204) as described in claims 14 or 15, is characterized in that,
Branching portion between described row (71d) is formed as: the flow path length till the entrance of described the second heat-transfer pipe of exporting to of described the first heat-transfer pipe (71) (72) from indoor heat converter (42,142,242) described in flow path length till the entrance of described the 3rd heat-transfer pipe (73) of exporting to of described the first heat-transfer pipe is when in refrigeration works as the evaporimeter of cold-producing medium is long.
17. 1 kinds of ceiling built-in air-conditioning systems, there is the structure that the indoor heat converter (42,142,242) consisting of fin tube type heat exchanger is disposed at the outer circumferential side of overlooking the centrifugal blower (41,141,241) while observing, it is characterized in that
Described indoor heat converter has following structure:
The many heat-transfer pipes (71,72,73) that flow therein for cold-producing medium are arranged in multistage on above-below direction, and are arranged with three row in the flow direction of the air blowing out from described centrifugal blower,
The refrigerant inlet of the described indoor heat converter in the case of indoor heat converter described in when refrigeration works as the evaporimeter of cold-producing medium is connected with many liquid refrigerant pipes (91), these many liquid refrigerant pipes (91) are connected with the heat-transfer pipe (71) that the row of weather side in the flow direction of described air are first row
Described in when refrigeration, the refrigerant outlet of indoor heat converter is connected with many gas refrigerant pipes (92,93), a part in these many gas refrigerant pipes (92,93) is that secondary series side gas refrigerant pipe is connected with the heat-transfer pipe (72) of secondary series in the flow direction of described air
Remainder in described many gas refrigerant pipes i.e. the 3rd row side gas refrigerant pipe is that tertial heat-transfer pipe (73) is connected with the row of downwind side in the flow direction of described air,
During refrigeration, flow through the heat-transfer pipe secondary series side heat-transfer pipe (71a) in the heat-transfer pipe that cold-producing medium after the part secondary series side liquid refrigerant pipe (91a) in described many liquid refrigerant pipes (91) is transported to described first row, and flowing through after described secondary series side heat-transfer pipe, in the outlet of described secondary series side heat-transfer pipe, by branching portion in secondary series (71g), be branched off into the heat-transfer pipe (72) of two described secondary series
The cold-producing medium that is transported to the heat-transfer pipe of two described secondary series is flowing through after the heat-transfer pipe of two described secondary series, from the outlet of the heat-transfer pipe of two described secondary series, is transported to described secondary series side gas refrigerant pipe (92),
During refrigeration, flow through heat-transfer pipe the 3rd row side heat-transfer pipe (71b) that cold-producing medium after remainder the 3rd row side liquid refrigerant pipe (91b) in described many liquid refrigerant pipes is transported to the described first row different from described secondary series side heat-transfer pipe, and flowing through after described the 3rd row side heat-transfer pipe, in the outlet of described the 3rd row side heat-transfer pipe, by the 3rd Lie Nei branching portion branch to a two described tertial heat-transfer pipe (73)
The cold-producing medium that is transported to two described tertial heat-transfer pipes is flowing through after two described tertial heat-transfer pipes, from the outlet of two described tertial heat-transfer pipes, is transported to described the 3rd row side gas refrigerant pipe (93).
18. ceiling built-in air-conditioning systems as claimed in claim 17 (4,104,204), is characterized in that,
The bore of described the 3rd row side liquid refrigerant pipe (91b) is than little at the bore of upside or the adjacent described secondary series side liquid refrigerant pipe (91a) of downside, or the length of tube of described the 3rd row side liquid refrigerant pipe (91b) is than long at the length of tube of upside or the adjacent described secondary series side liquid refrigerant pipe (91a) of downside.
CN201080026832.0A 2009-06-19 2010-06-16 Ceiling-mounted air conditioning unit Active CN102460026B (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
JP2009146787 2009-06-19
JP2009-146787 2009-06-19
PCT/JP2010/004005 WO2010146852A1 (en) 2009-06-19 2010-06-16 Ceiling-mounted air conditioning unit

Publications (2)

Publication Number Publication Date
CN102460026A CN102460026A (en) 2012-05-16
CN102460026B true CN102460026B (en) 2014-05-07

Family

ID=43356183

Family Applications (1)

Application Number Title Priority Date Filing Date
CN201080026832.0A Active CN102460026B (en) 2009-06-19 2010-06-16 Ceiling-mounted air conditioning unit

Country Status (9)

Country Link
US (1) US9528769B2 (en)
EP (1) EP2444751B1 (en)
JP (1) JP5423792B2 (en)
KR (1) KR101345541B1 (en)
CN (1) CN102460026B (en)
AU (1) AU2010261177B2 (en)
ES (1) ES2722223T3 (en)
TR (1) TR201905263T4 (en)
WO (1) WO2010146852A1 (en)

Families Citing this family (28)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP5267690B2 (en) 2012-02-03 2013-08-21 ダイキン工業株式会社 Indoor unit
JP5494705B2 (en) * 2012-03-16 2014-05-21 ダイキン工業株式会社 Two-way blowout ceiling air conditioner
WO2013190830A1 (en) * 2012-06-18 2013-12-27 パナソニック株式会社 Heat exchanger and air conditioner
CN103673077B (en) * 2012-09-10 2016-12-21 珠海格力电器股份有限公司 Vertical air conditioner
KR101988034B1 (en) * 2012-11-19 2019-06-11 엘지전자 주식회사 Air conditioner
US20150362222A1 (en) * 2013-01-22 2015-12-17 Mitsubishi Electric Corporation Refrigerant distribution device and a heat pump apparatus using the same refrigerant distribution device
JP5644889B2 (en) * 2013-04-30 2014-12-24 ダイキン工業株式会社 Air conditioner indoor unit
CN105683639B (en) * 2013-10-29 2018-01-19 三菱电机株式会社 Pipe joint, heat exchanger and air-conditioning device
JP6180338B2 (en) * 2014-01-29 2017-08-16 ジョンソンコントロールズ ヒタチ エア コンディショニング テクノロジー（ホンコン）リミテッド Air conditioner
GB2542312A (en) * 2014-07-18 2017-03-15 Mitsubishi Electric Corp Refrigeration cycle device
GB2537105A (en) * 2015-03-30 2016-10-12 Mcgowan Gregory Air conditioning system
JP2016200338A (en) * 2015-04-13 2016-12-01 ジョンソンコントロールズ ヒタチ エア コンディショニング テクノロジー（ホンコン）リミテッド Air conditioner
JP6573484B2 (en) * 2015-05-29 2019-09-11 日立ジョンソンコントロールズ空調株式会社 Heat exchanger
EP3348935B1 (en) * 2015-09-10 2021-01-27 Hitachi-Johnson Controls Air Conditioning, Inc. Heat exchanger
JP6639865B2 (en) * 2015-10-30 2020-02-05 東芝キヤリア株式会社 Indoor unit of air conditioner
WO2017168669A1 (en) * 2016-03-31 2017-10-05 三菱電機株式会社 Heat exchanger and refrigeration cycle apparatus
DE102016111136A1 (en) * 2016-06-17 2017-12-21 Güntner Gmbh & Co. Kg Air cooler for cooling the air in rooms, especially in walk-in storage or cold storage rooms
US11892178B2 (en) * 2016-12-28 2024-02-06 Daikin Industries, Ltd. Heat exchanger unit and air conditioner using the same
WO2018142567A1 (en) * 2017-02-03 2018-08-09 三菱電機株式会社 Air conditioner device
CN110462309B (en) * 2017-03-27 2022-03-01 大金工业株式会社 Heat exchanger and refrigerating apparatus
EP3604969A4 (en) * 2017-03-27 2020-04-01 Daikin Industries, Ltd. Air-conditioning indoor unit
EP3604996A4 (en) 2017-03-27 2020-03-25 Daikin Industries, Ltd. Heat exchanger and refrigeration device
JPWO2019030793A1 (en) 2017-08-07 2020-05-28 三菱電機株式会社 Heat exchanger, air conditioner indoor unit, and air conditioner
JP7078840B2 (en) 2018-01-19 2022-06-01 ダイキン工業株式会社 Heat exchanger and air conditioner
US11874001B1 (en) * 2018-10-22 2024-01-16 Epic Systems, Llc Temperature control system
KR102057506B1 (en) * 2019-02-28 2019-12-19 주식회사 하이옥스 Evaporator for ceiling-mounted thermo-hygrostat
CN116761967A (en) * 2021-02-10 2023-09-15 三菱电机株式会社 Outdoor heat exchanger and air conditioner
DE102021133803A1 (en) 2021-12-20 2023-06-22 Stiebel Eltron Gmbh & Co. Kg Finned tube heat exchanger, evaporator and heat pump

Citations (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH0478423U (en) * 1990-11-22 1992-07-08
JPH04359798A (en) * 1991-06-04 1992-12-14 Sharp Corp Air conditioner
JPH1151412A (en) * 1997-08-04 1999-02-26 Hitachi Ltd Indoor unit for air-conditioner, and its indoor heat exchanger
JP2000111206A (en) * 1998-10-06 2000-04-18 Toshiba Ave Co Ltd Embedment-in-ceiling type air conditioner
JP2000154991A (en) * 1998-11-20 2000-06-06 Kimura Kohki Co Ltd Heat exchanging coil for small water quantity fan coil unit
JP2000227230A (en) * 1999-02-02 2000-08-15 Kimura Kohki Co Ltd Heat exchange coil for air-conditioner
JP2001174047A (en) * 1999-12-17 2001-06-29 Matsushita Electric Ind Co Ltd Indoor unit of air conditioner
JP2005133976A (en) * 2003-10-28 2005-05-26 Hitachi Ltd Air-conditioner
CN2869709Y (en) * 2006-01-01 2007-02-14 海信集团有限公司 Air-conditioner indoor-set heat exchanger
CN101158502A (en) * 2007-10-15 2008-04-09 海信集团有限公司 Heat converter for outdoor machine of air-conditioner and outdoor aerials using the same

Family Cites Families (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4483156A (en) * 1984-04-27 1984-11-20 The Trane Company Bi-directional variable subcooler for heat pumps
DE3938842A1 (en) * 1989-06-06 1991-05-29 Thermal Waerme Kaelte Klima CONDENSER FOR A VEHICLE AIR CONDITIONING REFRIGERANT
US4995453A (en) * 1989-07-05 1991-02-26 Signet Systems, Inc. Multiple tube diameter heat exchanger circuit
JPH062016U (en) * 1992-06-05 1994-01-14 株式会社富士通ゼネラル Embedded type air conditioner
JP3423207B2 (en) * 1998-02-09 2003-07-07 クボタ空調株式会社 Heat exchanger coil structure
JPH11257800A (en) 1998-03-09 1999-09-24 Sanyo Electric Co Ltd Heat exchanger and air conditioner with exchanger
JP2000011120A (en) * 1998-06-25 2000-01-14 Toppan Printing Co Ltd Capacitive data card
JP4945357B2 (en) 2007-07-25 2012-06-06 三洋電機株式会社 Indoor unit of ceiling-embedded air conditioner
US20160123645A1 (en) * 2014-10-29 2016-05-05 Lg Electronics Inc. Air conditioner and method of controlling the same

Patent Citations (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH0478423U (en) * 1990-11-22 1992-07-08
JPH04359798A (en) * 1991-06-04 1992-12-14 Sharp Corp Air conditioner
JPH1151412A (en) * 1997-08-04 1999-02-26 Hitachi Ltd Indoor unit for air-conditioner, and its indoor heat exchanger
JP2000111206A (en) * 1998-10-06 2000-04-18 Toshiba Ave Co Ltd Embedment-in-ceiling type air conditioner
JP2000154991A (en) * 1998-11-20 2000-06-06 Kimura Kohki Co Ltd Heat exchanging coil for small water quantity fan coil unit
JP2000227230A (en) * 1999-02-02 2000-08-15 Kimura Kohki Co Ltd Heat exchange coil for air-conditioner
JP2001174047A (en) * 1999-12-17 2001-06-29 Matsushita Electric Ind Co Ltd Indoor unit of air conditioner
JP2005133976A (en) * 2003-10-28 2005-05-26 Hitachi Ltd Air-conditioner
CN2869709Y (en) * 2006-01-01 2007-02-14 海信集团有限公司 Air-conditioner indoor-set heat exchanger
CN101158502A (en) * 2007-10-15 2008-04-09 海信集团有限公司 Heat converter for outdoor machine of air-conditioner and outdoor aerials using the same

Also Published As

Publication number Publication date
TR201905263T4 (en) 2019-05-21
EP2444751A4 (en) 2016-07-20
EP2444751B1 (en) 2019-01-30
WO2010146852A1 (en) 2010-12-23
JP5423792B2 (en) 2014-02-19
AU2010261177A1 (en) 2012-02-02
ES2722223T3 (en) 2019-08-08
KR101345541B1 (en) 2013-12-26
AU2010261177B2 (en) 2013-07-18
US20120073786A1 (en) 2012-03-29
EP2444751A1 (en) 2012-04-25
JPWO2010146852A1 (en) 2012-11-29
US9528769B2 (en) 2016-12-27
CN102460026A (en) 2012-05-16

Similar Documents

Publication Publication Date Title
CN102460026B (en) Ceiling-mounted air conditioning unit
JP6352401B2 (en) Air conditioner
US8205470B2 (en) Indoor unit for air conditioner
CN203396065U (en) Heat exchanger, indoor unit and refrigerating cycle device
JP5257491B2 (en) Refrigeration equipment outdoor unit
CN110476026B (en) Heat exchanger unit
JP5447569B2 (en) Air conditioner heat exchanger and air conditioner
WO2019142642A1 (en) Indoor heat exchanger and air conditioning device
CN103998875B (en) Refrigerating plant
CN104185765A (en) Refrigeration device
WO2019239990A1 (en) Indoor heat exchanger and air conditioning device
CN1328548C (en) Air conditioner and outdoor unit therefor
JP6157593B2 (en) Heat exchanger and refrigeration cycle air conditioner using the same
JP6198976B2 (en) Heat exchanger and refrigeration cycle apparatus
CN108603726A (en) Heat exchanger
KR101425043B1 (en) Outdoor heat exchanger
WO2019240055A1 (en) Heat exchanger and air conditioner
JP2016148483A (en) Freezer unit
KR101425041B1 (en) Outdoor heat exchanger
JP6956866B2 (en) Refrigeration cycle equipment
JP7104331B2 (en) Refrigerator heat source unit
JP7078841B2 (en) Refrigeration equipment
CN115298486A (en) Outdoor unit of air conditioner
JPWO2021234952A5 (en)
JP2019132512A (en) Refrigeration device

Legal Events

Date Code Title Description
C06 Publication
PB01 Publication
C10 Entry into substantive examination
SE01 Entry into force of request for substantive examination
C14 Grant of patent or utility model
GR01 Patent grant